TW202104808A - Chilled water system - Google Patents

Abstract

A chilled water system includes a chiller, a heat exchange device, a first inlet control valve, a second inlet control valve, a first outlet control valve and a second outlet control valve. The chiller has a chiller inlet and a chiller outlet. The heat exchange device has a device inlet and a device outlet. The first inlet control valve communicates with the chiller inlet. The second inlet control valve is disposed in a flow path between the chiller inlet and the device outlet. The first outlet control valve is in communication with the chiller outlet. The second outlet control valve is disposed at a flow path between the chiller outlet and the device inlet. When the first inlet control valve and the first outlet control valve are at one of opening state and closing state, the second inlet control valve and the second outlet control valve are at the other of opening state and closing state.

Description

Ice water system

The present invention relates to an ice water system, and particularly relates to an ice water system with multiple sets of control valves.

The current ice water system includes several ice water machines to provide low-temperature cooling fluid to cool several different objects, such as mechanical devices, electronic devices, or external fluids (such as air). The temperature of the cooling fluid required by these objects to be cooled is different. However, the ice water system usually has to provide the cooling fluid with the lowest temperature demand, which is a waste of energy for other objects that do not require such low temperature cooling requirements. This will result in the unit energy consumption (Kw/RT) of the ice water system. Higher issues. Therefore, proposing an ice water system that can increase efficiency is one of the goals of the industry in this field.

The embodiment of the present invention provides an ice water system, which can improve the aforementioned conventional problems.

An embodiment of the present invention provides an ice water system. The ice water system includes a first ice water machine, a heat exchange device, a first inlet control valve, a second inlet control valve, a first outlet control valve, and a second outlet control valve. The first water ice machine has a first water ice machine inlet and a first water ice machine outlet. The heat exchange device has a first device inlet and a first device outlet. The first inlet control valve communicates with the inlet of the first ice water machine. The second inlet control valve is arranged in the flow path between the inlet of the first ice water machine and the outlet of the first device. The first outlet control valve is connected to the outlet of the first ice water machine. The second outlet control valve is arranged in the flow path between the outlet of the first chiller and the inlet of the first device. When the first inlet control valve and the first outlet control valve are at one of open and closed, the second inlet control valve and the second outlet control valve are at the other of open and closed.

In order to have a better understanding of the above and other aspects of the present invention, the following specific examples are given in conjunction with the accompanying drawings to describe in detail as follows:

In order to have a better understanding of the above-mentioned and other aspects of the present invention, the following specific embodiments are described in detail in conjunction with the accompanying drawings.

Please refer to Figures 1A~1E and Figures 2A~2E. Figure 1A shows a flow diagram of the ice water system 100 in a dual temperature mode according to an embodiment of the present invention. Figure 1B shows a part 1B of Figure 1A. Figure 1C shows an enlarged schematic diagram of part 1C of Figure 1A, Figure 1D shows an enlarged schematic diagram of part 1D' of Figure 1A, and Figure 1E shows a partial 1E' of Figure 1A Enlarged schematic diagram of. Figure 2A shows the flow path diagram of the ice water system 100 of Figure 1A in a single temperature mode, Figure 2B shows an enlarged schematic diagram of part 2B' of Figure 2A, and Figure 2C shows part 2C of Figure 2A Figure 2D is an enlarged schematic view of part 2D' of Figure 2A, and Figure 2E is an enlarged schematic view of part 2E' of Figure 2A. The bold line in the figure represents the fluid flow path in which the fluid is flowing, and the thin line represents the pipeline where the fluid is not flowing (like a broken circuit).

As shown in Figure 1A, the ice water system 100 includes at least one first ice water machine 110, at least one heat exchange device 120, a first inlet control valve 130A, a first outlet control valve 130B, a second inlet control valve 140A, and a second inlet control valve 140A. Two outlet control valves 140B, at least one second ice water machine 150, at least one first heat exchanger 160A, 160B and 160C, at least one first pump (primary pump) 170A, at least one second pump (secondary pump) Pump) 170B, at least one third pump (three pumps) 170C, temperature detectors 180A, 180B and 180C, flow control valves 185A, 185B and 185C, check valve 190, first control valves 191A and 191B, The second control valves 192A and 192B, the third control valves 193A and 193B, the fourth control valve 194 and the fifth control valve 195.

The first ice water machine 110 has a first ice water machine inlet 110a and a first ice water machine outlet 110b. The heat exchange device 120 has a first device inlet 120a and a first device outlet 120b. The first inlet control valve 130A communicates with the inlet 110a of the first ice water machine. The second inlet control valve 140A is arranged in the flow path between the inlet 110a of the first chiller and the outlet 120b of the first device. The first outlet control valve 130B is connected to the outlet 110b of the first ice water machine. The second outlet control valve 140B is arranged in the flow path between the outlet 110b of the first chiller and the inlet 120a of the first device. In this embodiment, when the first inlet control valve 130A and the first outlet control valve 130B are at one of open and closed, the second inlet control valve 140A and the second outlet control valve 140B are at the other of open and closed, To switch the ice water system 100 between the dual temperature mode and the single temperature mode.

The first ice water machine 110 can cool the fluid entering from the first ice water machine inlet 110a into a cooling fluid, and the cooling fluid is output from the first ice water machine outlet 110b to the heat exchange device 120 to provide the heat exchange device 120 to an object It is used for heat exchange for cooling and/or dehumidification purposes, where the objects are, for example, electronic equipment, mechanical equipment, and/or outside air. In one embodiment, the performance (such as cooling performance) of the first ice water machine 110 and the second ice water machine 150 are the same, but they may be different. In an example, the first ice water machine 110 and the second ice water machine 150 may be completely the same ice water machine.

The heat exchange device 120 may be, for example, an outdoor air conditioning box, a dry cooling coil (DCC), a heat exchanger, or other heat exchange elements used in an air conditioning system or cooling system, wherein the heat exchanger and/ Or the heat exchange element is, for example, a heat exchange tube or a heat exchange disk, and the hybrid dry cooling coil is, for example, a non-hybrid dry cooling coil or a hybrid dry cooling coil. In an embodiment, the heat exchange device 120 includes at least one of an outdoor air conditioning box 120A, a non-mixed dry cooling coil 120B, a hybrid dry cooling coil 120C, and a heat exchanger 120D (second heat exchanger).

As shown in Figures 1A to 1E, the first inlet control valve 130A and the first outlet control valve 130B are closed, and the second inlet control valve 140A and the second outlet control valve 140B are opened, so that the ice water system 100 enters the dual temperature mode. In addition, in conjunction with the flow path operation in the dual temperature mode, as shown in Figures 1A to 1E, the first control valve 191A and the second control valve 192A in Figure 1C are opened and the third control valve 193A is closed, and the first control valve 193A in Figure 1D is closed. A control valve 191B and a second control valve 192B are opened and the third control valve 193B, the fourth control valve 194 and the fifth control valve 195 are closed.

The following describes the flow path relationship between the chiller and the outdoor air conditioning box 120A in the dual temperature mode (shown in bold in the figure). As shown in FIGS. 1A and 1B, the outdoor air-conditioning box 120A has a first device inlet 120a and a first device outlet 120b. The second ice water machine 150 has a second ice water machine inlet 150a and a second ice water machine outlet 150b. The first device inlet 120a is connected to the second chiller outlet 150b, so the cooling fluid L11 output from the second chiller outlet 150b can enter the outside air conditioning box 120A from the first device inlet 120a. In addition, the first device outlet 120b is in communication with the second chiller inlet 150a, so the return fluid L12 flowing out of the first device outlet 120b can enter the second chiller 150 through the second chiller inlet 150a to receive Cooling of the second ice water machine 150.

In detail, as shown in the flow paths shown in FIGS. 1A and 1B, the second chiller 150 outputs the cooling fluid L11 from the first device inlet 120a into the outdoor air conditioning box 120A. Since the outside air conditioning box 120A provides first-class outside air (not shown) through the outside air conditioning box 120A with a dehumidification function, the temperature of the cooling fluid L11 must be low enough, for example, 6 degrees Celsius, but it depends on demand. Below or above 6 degrees Celsius. The cooling fluid L11 becomes the return fluid L12 after passing through the outside air conditioning box 120A (the state may change after the cooling fluid L11 exchanges heat with the outside air), and then flows out from the first device outlet 120b of the outside air conditioning box 120A and returns to the second The ice water machine 150 is cooled by the second ice water machine 150 into a cooling fluid L11. Since the first inlet control valve 130A and the first outlet control valve 130B are closed, the return fluid L12 cannot enter the first ice water machine 110 through the first inlet control valve 130A. In addition, since the outdoor air conditioning box 120A requires a sufficiently low-temperature cooling fluid, and the cooling fluid L21 output by the first ice water machine 110 has a relatively high temperature, the first device inlet 120a is not connected to the second outlet control valve 140B. In this way, even if the second outlet control valve 140B is in an open state, the higher-temperature cooling fluid L21 output by the first chiller 110 will not be output to the outdoor air conditioning box 120A.

In addition, as shown in Figures 1A and 1B, the first pump 170A can be arranged in the flow path between the inlet 150a of the second ice machine and the outlet 120b of the first device for the return flow from the outlet 120b of the first device. Fluid L12 is pressurized. In detail, the first pump 170A can help the return fluid L12 flowing from the outlet 120b of the first device to quickly enter the second ice water machine 150 and increase the flow of fluid into the second ice water machine 150. As shown in Figs. 1A and 1B, the second pump 170B can be arranged in the flow path between the outlet 150b of the second ice machine and the inlet 120a of the first device to protect the cooling fluid L11 from the second ice machine 150. Supercharged. In detail, the second pump 170B can help the cooling fluid L11 flowing out of the second ice water machine 150 quickly enter the outside air conditioning box 120A and increase the fluid flow into the outside air conditioning box 120A.

The following describes the flow path relationship between the chiller and the non-hybrid dry cooling coil 120B in the dual mode mode (shown in bold in the figure). As shown in Figures 1A and 1C, the first control valve 191A is arranged in the flow path between the second exchanger inlet 160a2 of the first heat exchanger 160A and the second outlet control valve 140B, and the second control valve 192A is arranged in the non- The flow path between the first device outlet 120b and the second inlet control valve 140A of the hybrid dry cooling coil 120B, and the third control valve 193A is arranged at the outlet end of the first control valve 191A and the inlet of the second control valve 192B The flow path between the ends. In order to cooperate with the flow path operation in the dual temperature mode, the first control valve 191A and the second control valve 192A are opened, and the third control valve 193A is closed. Since the third control valve 193A is closed, the reflux fluid L22 flowing out of the outlet 120b of the first device will not pass through the third control valve 193A and mix with the cooling fluid L21 (if mixing will increase the temperature of the cooling fluid L21, reduce the cooling fluid L21 Cooling capacity).

As shown in Figures 1A and 1C, the non-hybrid dry cooling coil 120B has a first device inlet 120a and a first device outlet 120b. The second ice water machine 150 has a second ice water machine inlet 150a and a second ice water machine outlet 150b. The first heat exchanger 160A includes a first exchanger inlet 160a1 and a first exchanger outlet 160b1 that are connected, and a second exchanger inlet 160a2 and a second exchanger outlet 160b2 that are connected. The second outlet control valve 140B is arranged in the flow path between the outlet 110b of the first chiller and the second exchanger inlet 160a2 of the first heat exchanger 160A, so that the cooling fluid L21 output from the outlet 110b of the first chiller passes through The second outlet control valve 140B and the second exchanger inlet 160a2 enter the first heat exchanger 160A. The second exchanger outlet 160b2 communicates with the first device inlet 120a, so that the cooling fluid L21' flowing out of the second exchanger outlet 160b2 enters the non-mixed dry cooling coil 120B through the first device inlet 120a. The second ice water machine inlet 150a is connected to the first exchanger outlet 160b1, and the second ice water machine outlet 150b is connected to the first exchanger inlet 160a1, so that the cooling fluid L21 output by the second ice water machine 150 can pass through the first exchanger inlet 160a1 enters the first heat exchanger 160A, and then flows out from the outlet 160b1 of the first exchanger and returns to the second ice water machine 150.

In detail, as shown in the flow paths shown in Figures 1A and 1C, the cooling fluid L11 output from the second ice water machine 150 flows through the first heat exchanger 160A, and the cooling fluid L21 output from the first ice water machine 110 passes through the first heat exchanger. After the second outlet control valve 140B flows through the first heat exchanger 160A. In this way, the cooling fluid L21 exchanges heat with the cooling fluid L11 in the first heat exchanger 160A, so that the temperature of the cooling fluid L21' after the heat exchange is adjusted to a desired temperature to meet the requirements of the non-mixed dry cooling coil 120B. demand. The non-mixed dry cooling coil 120B provides a cooling function of first-rate external air (not shown) passing through the non-mixed dry cooling coil 120B. Compared with the demand of the dehumidification function, the temperature of the cooling fluid L21' required for the cooling function is allowed to be higher, for example, 12 degrees Celsius, but depending on the demand, it can also be lower or higher than 12 degrees Celsius. After the cooling fluid L21 exchanges heat with the cooling fluid L11 in the first heat exchanger 160A, it becomes the cooling fluid L21', and then flows out from the second exchanger outlet 160b2 and enters the non-mixed dry cooling coil through the first device inlet 120a 120B. The cooling fluid L21' becomes the reflux fluid L22 after passing through the non-mixing dry cooling coil 120B (the state may change after the heat exchange with the outside air). Then, the reflux fluid L22 flows out from the first device outlet 120b of the non-mixed dry cooling coil 120B and flows back to the first ice water machine 110 to be cooled by the first ice water machine 110.

Compared with the reflux fluid L12 returning from the outdoor air conditioning box 120A, the reflux fluid L22 returning from the non-hybrid dry cooling coil 120B has a higher temperature, so that the cooling fluid L21 cooled by the first ice water machine 110 has a higher temperature. The temperature is also higher than the temperature of the cooling fluid L11 cooled by the second chiller 150. In one embodiment, the temperature of the return fluid L12 is, for example, 12 degrees Celsius, the return fluid L12 becomes the cooling fluid L11 after being cooled by the second ice water machine 150, the temperature of which is, for example, 6 degrees Celsius, and the temperature of the return fluid L22 is, for example It is 18 degrees Celsius, and the reflux fluid L22 becomes the cooling fluid L21 after being cooled by the first ice water machine 110, and its temperature is, for example, 12 degrees Celsius. Depending on requirements and/or actual conditions, the embodiment of the present invention does not limit the aforementioned temperature value.

As shown in FIGS. 1A and 1C, the temperature detector 180A can be disposed in the monitoring flow path F1 between the second exchanger outlet 160b2 and the first device inlet 120a, and used to detect the temperature of the monitoring flow path F1. The flow control valve 185A is arranged in the control flow path F2 between the first exchanger outlet 160b1 and the second chiller inlet 150a, and is used to control the control flow path F2 according to the detected temperature of the monitoring flow path F1 flow. For example, when the temperature detector 180A detects that the temperature of the monitoring flow path F1 is higher than the expected temperature (such as 12 degrees Celsius), the flow control valve 185A expands the opening of the valve port to allow more low-temperature cooling fluid L11 to flow Through the first heat exchanger 160A, the temperature of the cooling fluid L21 passing through the first heat exchanger 160A is reduced to make it close to the expected temperature. Conversely, when the temperature detector 180A detects that the temperature of the monitoring flow path F1 is lower than 12 degrees Celsius, the flow control valve 185A reduces the opening of the valve port to reduce the low-temperature cooling fluid L11 flowing through the first heat exchanger 160A. The flow rate in turn increases the temperature of the cooling fluid L21 passing through the first heat exchanger 160A, bringing it close to the expected temperature.

In addition, as shown in Figures 1A and 1C, the first pump 170A can be arranged in the flow path between the inlet 110a of the first ice machine and the inlet control valve (the first inlet control valve 130A and the second inlet control valve 140A) , Used to pressurize the return fluid from the inlet control valve. In detail, the first pump 170A can help the return fluid L22 flowing out of the outlet 120b of the first device to quickly enter the first ice water machine 110 and increase the fluid flow into the first ice water machine 110. As shown in Figures 1A and 1C, the second pump 170B is arranged in the flow path between the second chiller outlet 150b and the first exchanger inlet 160a1 of the first heat exchanger 160A, in order to The cooling fluid L11 at the outlet 150b of the chiller is pressurized. In detail, the second pump 170B can help the cooling fluid L11 flowing out of the second ice water machine 150 quickly enter the first heat exchanger 160A and can increase the fluid flow into the first heat exchanger 160A.

As shown in Figures 1A and 1C, the third pump 170C is arranged in the flow path between the second exchanger inlet 160a2 and the second outlet control valve 140B, and is used to treat the cooling fluid from the second outlet control valve 140B Supercharged. In detail, the third pump 170C can help the cooling fluid L21 flowing out of the first ice water machine 110 to quickly enter the first heat exchanger 160A and can increase the fluid flow into the first heat exchanger 160A. As shown in the figure, due to the configuration of the third pump 170C, the flow path between the first ice water machine 110 and the first heat exchanger 160A does not require an additional pump. For example, there is no need to configure any pumps in the area R1 in Figure 1A.

The following describes the flow path relationship between the chiller and the hybrid dry cooling coil 120C in the dual temperature mode (shown in bold in the figure). As shown in Figures 1A and 1D, the first control valve 191B is arranged in the flow path between the second exchanger inlet 160a2 and the second outlet control valve 140B of the first heat exchanger 160B, and the second control valve 192B is arranged in the mixing The flow path between the first device outlet 120b of the dry type cooling coil 120C and the second inlet control valve 140A, and the third control valve 193B is arranged at the outlet end of the first control valve 191A and the inlet end of the second control valve 192B The flow path between. The fourth control valve 194 is arranged in the flow path between the inlet end of the one-way valve 190 and the inlet of the ice water machine (such as the first ice water machine inlet 110a and the second ice water machine inlet 150a), and the fifth control valve 195 is arranged There is a flow path between the outlet end of the one-way valve 190 and the outlet of the ice water machine (such as the first ice water machine outlet 110b and the second ice water machine outlet 150b). In order to cooperate with the flow path operation in the dual temperature mode, the first control valve 191B and the second control valve 192B are opened, and the third control valve 193B, the fourth control valve 194 and the fifth control valve 195 are closed. Since the third control valve 193B is closed, the reflux fluid L22 flowing out of the outlet 120b of the first device will not pass through the third control valve 193B and mix with the cooling fluid L21 (if mixing will increase the temperature of the cooling fluid L21, reduce the cooling fluid L21 Cooling capacity). Since the fourth control valve 194 and the fifth control valve 195 are closed, the cooling fluid L21 can only enter the first heat exchanger 160B via the check valve 190.

In detail, the hybrid dry cooling coil 120C has a first device inlet 120a and a first device outlet 120b. The second ice water machine 150 has a second ice water machine inlet 150a and a second ice water machine outlet 150b. The first heat exchanger 160B includes a first exchanger inlet 160a1 and a first exchanger outlet 160b1 that are connected, and a second exchanger inlet 160a2 and a second exchanger outlet 160b2 that are connected. The second outlet control valve 140B is arranged in the flow path between the outlet 110b of the first ice machine and the second exchanger inlet 160a2 of the first heat exchanger 160B, so that the cooling fluid L21 output from the outlet 110b of the first ice machine passes through The second outlet control valve 140B and the second exchanger inlet 160a2 enter the first heat exchanger 160B. The second exchanger outlet 160b2 communicates with the first device inlet 120a, so that the cooling fluid L21' flowing out of the second exchanger outlet 160b2 enters the hybrid dry cooling coil 120C through the first device inlet 120a. The second ice water machine inlet 150a is connected to the first exchanger outlet 160b1, and the second ice water machine outlet 150b is connected to the first exchanger inlet 160a1, so that the cooling fluid L11 output by the second ice water machine 150 can pass through the first exchanger inlet 160a1 enters the first heat exchanger 160B, and then flows out from the outlet 160b1 of the first exchanger and returns to the second ice water machine 150.

In detail, as shown in the flow paths shown in Figures 1A and 1D, the cooling fluid L11 output from the second ice water machine 150 flows through the first heat exchanger 160B, and the cooling fluid L21 output from the first ice water machine 110 passes through the first heat exchanger 160B. After the second outlet control valve 140B flows through the first heat exchanger 160B. In this way, the cooling fluid L21 exchanges heat with the cooling fluid L11 in the first heat exchanger 160B, so that the temperature of the cooling fluid L21' after the heat exchange is adjusted to a desired temperature to meet the requirements of the hybrid dry cooling coil 120C. The hybrid dry cooling coil 120C provides a cooling function of first-rate external air (not shown) passing through the hybrid dry cooling coil 120C. Compared with the demand of the dehumidification function, the temperature of the cooling fluid L21' required for the cooling function is allowed to be higher, for example, 12 degrees Celsius, but depending on the demand, it can also be lower or higher than 12 degrees Celsius. The cooling fluid L21 exchanges heat with the cooling fluid L11 in the first heat exchanger 160B and becomes the cooling fluid L21', flows out from the second exchanger outlet 160b2 and enters the hybrid dry cooling coil 120C through the first device inlet 120a. The cooling fluid L21' becomes the reflux fluid L22 after passing through the hybrid dry cooling coil 120C (the state may change after the heat exchange with the outside air). Then, the reflux fluid L22 flows out from the first device outlet 120b of the hybrid dry cooling coil 120C and flows back to the first ice water machine 110 to be cooled by the first ice water machine 110.

Compared with the reflux fluid L12 returning from the outdoor air conditioning box 120A, the reflux fluid L22 returning from the hybrid dry cooling coil 120C has a higher temperature, so that the cooling fluid L21 cooled by the first ice water machine 110 has a higher temperature. The temperature is also higher than the temperature of the cooling fluid L11 cooled by the second chiller 150.

As shown in FIGS. 1A and 1D, the temperature detector 180B can be disposed in the monitoring flow path F1 between the second exchanger outlet 160b2 and the first device inlet 120a, and used to detect the temperature of the monitoring flow path F1. The flow control valve 185B is arranged in the control flow path F2 between the first exchanger outlet 160b1 and the second chiller inlet 150a, and is used to control the control flow path F2 according to the detected temperature of the monitoring flow path F1 flow. For example, when the temperature detector 180B detects that the temperature of the monitoring flow path F1 is higher than the expected temperature (such as 12 degrees Celsius), the flow control valve 185B expands the opening of the valve port to allow more low-temperature cooling fluid L11 to flow Through the first heat exchanger 160B, the temperature of the cooling fluid L21 passing through the first heat exchanger 160B is reduced to make it close to the expected temperature. Conversely, when the temperature detector 180B detects that the temperature of the monitoring flow path F1 is lower than 12 degrees Celsius, the flow control valve 185B reduces the opening of the valve port to reduce the low-temperature cooling fluid L11 flowing through the first heat exchanger 160B. The flow rate in turn increases the temperature of the cooling fluid L21 passing through the first heat exchanger 160B, bringing it close to the expected temperature.

In addition, as shown in Figures 1A and 1D, the second pump 170B is arranged in the flow path between the second chiller outlet 150b and the first exchanger inlet 160a1 of the first heat exchanger 160B to counter the flow path from the first heat exchanger 160B. The cooling fluid L11 at the outlet 150b of the second ice machine is pressurized. In detail, the second pump 170B can help the cooling fluid L11 flowing out of the second ice water machine 150 quickly enter the first heat exchanger 160B and can increase the fluid flow into the first heat exchanger 160B.

As shown in Figures 1A and 1D, the third pump 170C can be arranged in the flow path between the second exchanger inlet 160a2 and the second outlet control valve 140B, for example, in the second exchanger inlet 160a2 and the one-way valve. The flow path between the outlet ends of 190 is used to pressurize the cooling fluid from the second outlet control valve 140B (or the one-way valve 190). In detail, the third pump 170C can help the cooling fluid L21 flowing out of the first ice water machine 110 to quickly enter the first heat exchanger 160B and can increase the fluid flow into the first heat exchanger 160B. As shown in the figure, due to the configuration of the third pump 170C, the flow path between the first ice water machine 110 and the first heat exchanger 160B does not require an additional pump. For example, there is no need to configure any pumps in the area R1 in Figure 1A.

As shown in Figures 1A and 1D, the one-way valve 190 is arranged in the flow path between the second exchanger inlet 160a2 and the second outlet control valve 140B, and is used to allow a cooling fluid from the second outlet control valve 140B L21 flows unidirectionally into the second exchanger inlet 160a2.

The following describes the flow path relationship between the chiller and the heat exchanger 120D in the dual temperature mode (shown in bold in the figure). As shown in Figures 1A and 1E, the heat exchanger 120D is a second heat exchanger. The second heat exchanger includes a communicating first device inlet 120a and a first device outlet 120b, and a communicating third exchanger inlet 120c and The third switch outlet 120d. The second ice water machine 150 has a second ice water machine inlet 150a and a second ice water machine outlet 150b. The first device inlet 120a is connected to the first water chiller outlet 110b, so the cooling fluid L21 output from the first water chiller outlet 110b can enter the heat exchanger 120D from the first device inlet 120a. In addition, the first device outlet 120b is in communication with the first ice water machine inlet 110a, so the return fluid L21' flowing out of the first device outlet 120b can enter the first ice water machine 110 through the first ice water machine inlet 110a to It is cooled by a chiller 110.

The second ice water machine inlet 150a is connected to the first exchanger outlet 160b1, and the second ice water machine outlet 150b is connected to the first exchanger inlet 160a1, so that the cooling fluid L11 of the second ice water machine 150 can pass from the first exchanger inlet 160a1 Enter the first heat exchanger 160C, and then return to the second ice water machine 150 from the outlet 160b1 of the first exchanger.

The first heat exchanger 160C includes a first exchanger inlet 160a1 and a first exchanger outlet 160b1 that are connected, and a second exchanger inlet 160a2 and a second exchanger outlet 160b2 that are connected. The second exchanger outlet 160b2 is connected to the machine water inlet 10a of a machine 10, so that the cooling fluid L10' flowing out of the second exchanger outlet 160b2 enters the machine 10 through the machine water inlet 10a to cool the machine 10. The machine 10 is, for example, semiconductor processing equipment or any mechanical or electronic device that needs to be cooled. In an embodiment, the machine 10 may be a component of the ice water system 100, but may not be included in the ice water system 100.

As shown in Figures 1A and 1E, the second exchanger inlet 160a2 is connected to the third exchanger outlet 120d, and the third exchanger inlet 120c is connected to the machine outlet 10b of the machine 10. In this way, the return fluid L10'' flowing out of the machine outlet 10b of the machine 10 exchanges heat with the cooling fluid L11 in the first heat exchanger 160C to become the cooling fluid L10'. In an embodiment, the temperature of the cooling fluid L10' may be lower than that of the return fluid L10', and this low-temperature cooling fluid L10' enters the machine 10 to cool the machine 10.

Compared with the cooling requirements of the hybrid dry cooling coil, the temperature of the cooling fluid L10' required by the machine 10 is allowed to be higher, such as 18 degrees Celsius, but depending on the demand, it can be lower or higher than 18 degrees Celsius. degree. Since the temperature of the cooling fluid L10' required by the machine 10 is allowed to be higher, the reflux fluid L10" flowing out of the machine 10 does not need to pass through the ice water machine, and is provided by the heat exchanger 120D and the first heat exchanger 160C The heat exchange can make the temperature of the cooling fluid L10' flowing out of the outlet 160b2 of the second exchanger meet the cooling requirement of the machine 10.

As shown in Figures 1A and 1E, the temperature detector 180C can be arranged in the monitoring flow path F1 between the second exchanger outlet 160b2 and the machine water inlet 10a of the machine 10, and used to detect the monitoring flow path F1 temperature. The flow control valve 185C is arranged in the control flow path F2 between the first exchanger outlet 160b1 and the second chiller inlet 150a, and is used to control the control flow path F2 according to the detected temperature of the monitoring flow path F1 flow. For example, when the temperature detector 180C detects that the temperature of the monitoring flow path F1 is higher than the expected temperature (such as 18 degrees Celsius), the flow control valve 185C expands the opening of the valve port to allow more low-temperature cooling fluid L11 to flow Passing through the first heat exchanger 160C, the temperature of the reflux fluid L10" passing through the first heat exchanger 160C is lowered to be close to the expected temperature. Conversely, when the temperature detector 180C detects that the temperature of the monitoring flow path F1 is lower than 18 degrees Celsius, the flow control valve 185C reduces the opening of the valve port to reduce the low-temperature cooling fluid L11 flowing through the first heat exchanger 160C. The flow rate in turn increases the temperature of the return fluid L10" passing through the first heat exchanger 160C, bringing it close to the expected temperature.

As shown in Figs. 1A and 1E, the second pump 170B can be arranged in the flow path between the outlet 110b of the first ice machine and the inlet 120a of the first device to protect the cooling fluid L21 from the first ice machine 110. Supercharged. In detail, the second pump 170B can help the cooling fluid L21 flowing out of the first ice water machine 110 to quickly enter the heat exchanger 120D and can increase the fluid flow into the heat exchanger 120D.

As shown in Figures 1A and 1E, the third pump 170C is arranged in the flow path between the third exchanger inlet 120c and the machine outlet 10b of the machine 10 to prevent the return fluid from the machine outlet 10b. L10'' supercharged. In detail, the third pump 170C can help the return fluid L10" flowing out of the water outlet 10b to enter the heat exchanger 120D, the first heat exchanger 160C, and the machine 10 quickly in sequence, and can be added to the heat exchanger 120D. , The first heat exchanger 160C and the fluid flow rate in the machine table 10 to improve the cooling efficiency of the machine table 10.

In summary, in the dual temperature mode, for the external air conditioning box 120A, the second chiller 150 outputs the cooling fluid L11 to the external air conditioning box 120A via the second pump 170B (optional) to provide the external air conditioning box 120A 120A is used for dehumidification of outside air. The cooling fluid L11 passes through the outdoor air-conditioning box 120A and becomes the return fluid L12 and returns to the second ice water machine 150 to be cooled by the second ice water machine 150 to become the cooling fluid L11.

To sum up, in the dual temperature mode, taking the non-hybrid dry cooling coil 120B, the second chiller 150 outputs the cooling fluid L11 to the first heat exchanger 160A, and the cooling fluid L11 passes through the first heat exchanger 160A. It becomes the return fluid L12, and then returns to the second ice water machine 150. The first ice water machine 110 outputs the cooling fluid L21 to the first heat exchanger 160A. The cooling fluid L21 exchanges heat with the cooling fluid L11 in the first heat exchanger 160A and then becomes the cooling fluid L21', and the cooling fluid L21' flows to the non- The hybrid dry cooling coil 120B provides the non-hybrid dry cooling coil 120B for cooling an external air. The cooling fluid L21' passes through the non-mixed dry cooling coil 120B and becomes the reflux fluid L22 and returns to the first ice water machine 110 to be cooled by the first ice water machine 110 to become the cooling fluid L21.

To sum up, in the dual temperature mode, taking the hybrid dry cooling coil 120C, the second chiller 150 outputs the cooling fluid L11 to the first heat exchanger 160B, and the cooling fluid L11 becomes the first heat exchanger 160B after passing through the first heat exchanger 160B. The fluid L12 is returned and then returned to the second ice water machine 150. The first ice water machine 110 outputs the cooling fluid L21 to the first heat exchanger 160B. The cooling fluid L21 exchanges heat with the cooling fluid L11 in the first heat exchanger 160A to become the cooling fluid L21', and the cooling fluid L21' flows to the mixing The dry-type cooling coil 120C is used to provide the hybrid dry-type cooling coil 120C for cooling an external air. The cooling fluid L21' passes through the hybrid dry cooling coil 120C and becomes the reflux fluid L22 and returns to the first ice water machine 110 to be cooled by the first ice water machine 110 to become the cooling fluid L21.

In summary, in the dual temperature mode, taking the heat exchanger 120D as far as the heat exchanger 120D is concerned, the second ice water machine 150 outputs the cooling fluid L11 to the first heat exchanger 160C, and the cooling fluid L11 becomes the return fluid L12 after passing through the first heat exchanger 160C. , And then return to the second ice water machine 150. The first ice water machine 110 outputs the cooling fluid L21 to the heat exchanger 120D via the second pump 170B (optional). The cooling fluid L21 exchanges heat with the return fluid L10" in the heat exchanger 120D. The heat exchanged fluid L21 'Return the first ice water machine 110. The cooling fluid L10' flowing out of the first heat exchanger 160C flows to the machine 10 to cool the machine 10. The cooling fluid L10' passing through the machine 10 becomes the return fluid L10'', The reflux fluid L10" exchanges heat with the cooling fluid L21 in the heat exchanger 120D, and exchanges heat with the cooling fluid L11 in the first heat exchanger 160C to become the cooling fluid L10', and then flows to the machine 10 to Cooling machine 10.

In summary, with the dual-temperature mode flow path design of the embodiment of the present invention, the first ice water machine 110 and the second ice water machine 150 of the same specification can be used to output the cooling fluid L21 and the cooling fluid L11 of different temperatures, respectively, so as to achieve Dual temperature function.

In the single temperature mode, the first ice water machine 110 and the second ice water machine 150 both output the cooling fluid L21 and the cooling fluid L11 at the same temperature. The following further introduces the flow path design of the single temperature mode.

As shown in Figures 2A and 2B, in the single-temperature mode, the flow path relationship between the chiller and the outdoor air conditioning box 120A (shown in bold in the figure) is similar to the dual-temperature mode, and will not be repeated here.

The following describes the flow path relationship between the chiller and the non-hybrid dry cooling coil 120B in the single temperature mode (shown in bold in the figure). Different from the dual temperature mode, as shown in Figures 2A and 2C, in the single temperature mode, the first inlet control valve 130A and the first outlet control valve 130B are opened, while the second inlet control valve 140A and the second outlet control valve are opened. The valve 140B is closed, the first control valve 191A and the second control valve 192A are closed, and the third control valve 193A is open. Since the first control valve 191A and the second control valve 192A are closed and the third control valve 193A is opened, the return fluid L22 flowing out of the outlet 120b of the first device flows through the first heat exchanger 160A via the third control valve 193A. The first heat exchanger 160A performs non-mixed heat exchange with the cooling fluid L11.

The following describes the flow path relationship between the chiller and the hybrid dry cooling coil 120C in the single temperature mode (shown in bold in the figure). Different from the dual temperature mode, as shown in Figures 2A and 2D, in the single temperature mode, the first inlet control valve 130A and the first outlet control valve 130B are opened, while the second inlet control valve 140A and the second outlet control valve are opened. The valve 140B is closed, the first control valve 191B and the second control valve 192B are closed, and the third control valve 193B is opened. Since the first control valve 191B and the second control valve 192B are closed and the third control valve 193B, the fourth control valve 194 and the fifth control valve 195 are opened, the return fluid L22 flowing out of the first device outlet 120b passes through the third control valve 193B and the one-way valve 190 perform mixed heat exchange with the cooling fluid L11. It can be seen from this embodiment that in the single-temperature mode, the reflux fluid flowing from the outlet 120b of the first device performs a mixed heat exchange with the cooling fluid, but in the dual-temperature mode, the reflux fluid flowing from the first device outlet 120b and the cooling fluid perform non-exchange. Hybrid heat exchange, however, both modes share the same hybrid dry cooling coil 120C.

The following describes the flow path relationship between the chiller and the heat exchanger 120D in the single temperature mode (shown in bold in the figure). Different from the dual temperature mode, as shown in Figures 2A and 2E, in the single temperature mode, the first inlet control valve 130A and the first outlet control valve 130B are opened, while the second inlet control valve 140A and the second outlet control valve Valve 140B is closed. In this way, the return fluid L10'' flowing out of the machine 10 does not exchange heat with any cooling liquid in the heat exchanger 120D, but exchanges heat with the cooling fluid L11 in the first heat exchanger 160C.

To sum up, although the present invention has been disclosed as above by embodiments, it is not intended to limit the present invention. Those with ordinary knowledge in the technical field to which the present invention belongs can make various changes and modifications without departing from the spirit and scope of the present invention. Therefore, the scope of protection of the present invention shall be subject to those defined by the attached patent scope.

10: Machine 10a: machine inlet 10b: machine outlet 100: ice water system 110: The first ice water machine 110a: Entrance of the first chiller 110b: Exit of the first ice water machine 120: heat exchange device 120a: Entrance of the first device 120b: First device exit 120c: entrance of the third exchanger 120d: third switch outlet 120A: outside air conditioning box 120B: Non-mixed dry cooling coil 120C: Hybrid dry cooling coil 120D: Heat exchanger 130A: First inlet control valve 130B: The first outlet control valve 140A: second inlet control valve 140B: The second outlet control valve 150: The second ice water machine 150a: Entrance of the second chiller 150b: The second chiller outlet 160A, 160B, 160C: the first heat exchanger 160a1: entrance of the first exchanger 160b1: the first switch outlet 160a2: entrance to the second exchanger 160b2: second switch outlet 170A: The first pump 170B: second pump 170C: Third Pump 180A, 180B, 180C: temperature detector 185A, 185B, 185C: flow control valve 190: Check valve 191A, 191B: the first control valve 192A, 192B: second control valve 193A, 193B: third control valve 194: The fourth control valve 195: Fifth control valve L10’, L11, L21, L21’: Cooling fluid L10’’, L12, L22: return fluid F1: Monitor the flow path F2: Control flow path

FIG. 1A is a flow diagram of the ice water system in a dual temperature mode according to an embodiment of the present invention. Figure 1B is an enlarged schematic view of part 1B' of Figure 1A. Fig. 1C is an enlarged schematic diagram of a part 1C' of Fig. 1A. Fig. 1D shows an enlarged schematic diagram of a part 1D' of Fig. 1A. Fig. 1E is an enlarged schematic diagram of part 1E' of Fig. 1A. Figure 2A shows the flow path of the ice water system in Figure 1A in a single temperature mode. Figure 2B shows an enlarged schematic view of part 2B' of Figure 2A. Figure 2C shows an enlarged schematic view of part 2C' of Figure 2A. Figure 2D is an enlarged schematic view of a part 2D' of Figure 2A. Fig. 2E is an enlarged schematic diagram of part 2E' of Fig. 2A.

10: Machine

100: ice water system

110: The first ice water machine

110a: Entrance of the first chiller

110b: Exit of the first ice water machine

120: heat exchange device

120a: Entrance of the first device

120b: First device exit

120A: outside air conditioning box

120B: Non-mixed dry cooling coil

120C: Hybrid dry cooling coil

120D: Heat exchanger

130A: First inlet control valve

130B: The first outlet control valve

140A: second inlet control valve

140B: The second outlet control valve

150: The second ice water machine

150a: Entrance of the second chiller

150b: The second chiller outlet

160A, 160B, 160C: the first heat exchanger

170A: The first pump

170B: second pump

L11, L21: cooling fluid

Claims (17)

An ice water system, including: A first ice water machine, having a first ice water machine inlet and a first ice water machine outlet; A heat exchange device having a first device inlet and a first device outlet; A first inlet control valve connected to the inlet of the first ice water machine; A second inlet control valve arranged in the flow path between the inlet of the first ice water machine and the outlet of the first device; A first outlet control valve connected to the outlet of the first ice water machine; A second outlet control valve, which is arranged in the flow path between the outlet of the first chiller and the inlet of the first device; Wherein, when the first inlet control valve and the first outlet control valve are at one of open and closed, the second inlet control valve and the second outlet control valve are at the other of open and closed. The ice water system according to the first item of the patent application, wherein the temperature of the cooling fluid output from the second outlet control valve is higher than the temperature of the cooling fluid output from the first outlet control valve. The ice water system described in item 1 of the scope of patent application further includes: A first pump is arranged in the flow path between the inlet of the first ice water machine and the first inlet control valve to pressurize the fluid from the first inlet control valve. The ice water system described in item 1 of the scope of patent application further includes: A second ice water machine, having a second ice water machine inlet and a second ice water machine outlet; Wherein, the outlet of the first device is communicated with the inlet of the second ice water machine, and the inlet of the first device is communicated with the outlet of the second ice water machine but not connected with the second outlet control valve. The ice water system described in item 4 of the scope of patent application includes: A second pump is arranged in the flow path between the outlet of the second ice water machine and the inlet of the first device to pressurize a cooling fluid from the outlet of the second ice water machine. The ice water system described in item 4 of the scope of patent application, wherein the performance of the first ice water machine and the second ice water machine are the same. The ice water system described in item 1 of the scope of patent application further includes: A second ice water machine, having a second ice water machine inlet and a second ice water machine outlet; A first heat exchanger, including a first exchanger inlet and a first exchanger outlet communicating with each other, and a second exchanger inlet and a second exchanger outlet communicating with each other; Wherein, the second outlet control valve is arranged in the flow path between the outlet of the first ice machine and the inlet of the second exchanger of the first heat exchanger; the outlet of the second exchanger is in communication with the inlet of the first device ； Wherein, the inlet of the second ice water machine is connected to the outlet of the first exchanger, and the outlet of the second ice water machine is connected to the inlet of the first exchanger. The ice water system described in item 7 of the scope of patent application further includes: A temperature detector arranged in a monitoring flow path between the outlet of the second exchanger and the inlet of the first device, and used for detecting a temperature of the monitoring flow path; A flow control valve is arranged in a control flow path between the outlet of the first exchanger and the inlet of the second ice water machine, and is used for controlling the flow of the control flow path according to the temperature. The ice water system described in item 7 of the scope of patent application further includes: A second pump is arranged in the flow path between the outlet of the second ice water machine and the inlet of the first exchanger to pressurize the cooling fluid from the outlet of the second ice water machine. The ice water system described in item 7 of the scope of patent application further includes: A third pump is arranged in the flow path between the inlet of the second exchanger and the second outlet control valve, and is used to pressurize a cooling fluid from the second outlet control valve. The ice water system described in item 7 of the scope of patent application further includes: A one-way valve, arranged in the flow path between the inlet of the second exchanger and the second outlet control valve, and used to allow a cooling fluid from the second outlet control valve to flow into the second one-way Switch entrance. As described in item 11 of the scope of patent application, the ice water system further includes: A second pump is arranged in the flow path between the outlet of the second ice water machine and the inlet of the first exchanger to pressurize the cooling fluid from the outlet of the second ice water machine. As described in item 11 of the scope of patent application, the ice water system further includes: A third pump is arranged in the flow path between the inlet of the second exchanger and the one-way valve, and is used to pressurize a cooling fluid from the one-way valve. The ice water system described in item 1 of the scope of patent application further includes: A second ice water machine, having a second ice water machine inlet and a second ice water machine outlet; One machine with one machine inlet and one machine outlet; and A first heat exchanger, including a first exchanger inlet and a first exchanger outlet communicating with each other, and a second exchanger inlet communicating with a second exchanger outlet, the second exchanger outlet communicating with the Machine inlet; Wherein, the inlet of the second ice water machine is connected to the outlet of the first exchanger, and the outlet of the second ice water machine is connected to the inlet of the first exchanger; Wherein, the heat exchange device is a second heat exchanger, and the second heat exchanger further includes a third exchanger inlet communicating with a third exchanger outlet; the second exchanger inlet communicating with the third exchanger The outlet of the third exchanger is connected to the water outlet of the machine. The ice water system described in item 14 of the scope of patent application includes: A second pump is arranged in the flow path between the outlet of the first ice water machine and the inlet of the first device to pressurize the cooling fluid from the outlet of the first ice water machine. The ice water system described in item 14 of the scope of patent application includes: A third pump is arranged in the flow path between the inlet of the third exchanger and the water outlet of the machine, and is used to pressurize the fluid from the water outlet of the machine. The ice water system described in item 14 of the scope of patent application includes: A temperature detector arranged in a monitoring flow path between the outlet of the second exchanger and the water inlet of the machine, and used for detecting a temperature of the monitoring flow path; and A flow control valve is arranged in a control flow path between the outlet of the first exchanger and the inlet of the second ice machine, and is used to control the flow of the control flow path according to the temperature.

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