TW201712478A - Server cooling system - Google Patents

Abstract

As a server cooling system in which are disposed cold zones and hot zones grows in scale, cooling costs increase dramatically. Accordingly, there is a demand for a cooling system which has a high degree of efficiency in cooling. The present invention provides a server cooling system in which the interior of a chamber is effectively divided in two parts, with a cold aisle formed in one part, a hot aisle formed in the other part, and a server rack positioned on the boundary between the cold aisle and the hot aisle, wherein the server cooling system is characterized: by comprising an air conditioning device which is disposed on the hot aisle side, a circulation path which is disposed from the air conditioning device to the cold aisle, and a rack fan which is disposed on the hot aisle face of a heat radiating part of the server rack; and in that the rack fan reduces the airflow volume of the air conditioning device, and the airflow volume of the rack fan is less than or equal to the reduced airflow volume of the air conditioning device.

Description

Server cooling system

The present invention relates to a server cooling system in which a plurality of servers are stored in a server rack in a server center in which a plurality of servers are installed, and the server rack is disposed in a cooling chamber. The hot and cold channels are set indoors to cool the server.

Due to proposals such as cloud systems, the demand for data centers that aggregate multiple servers has increased. The server generates heat due to the large amount of current consumed. Therefore, a cooling system that combines and cools multiple servers is necessary. As such a cooling system, the proposed system is as follows: a hot zone and a cold zone are arranged in the casing, a server rack is arranged on the boundary thereof, and the server frame is cooled by using cold air from the cold zone, and The air which is heated by the heat exchange is cooled by the cooler in the hot zone, and is again supplied to the cold zone (Patent Document 1).

With such a cooling system, the servos are integrated into the respective housings. The advantages are as follows: the container is made into a container type, which makes the transportation simple; since the components can be properly designed beforehand, the energy saving is excellent; because a plurality of them are provided, the initial construction and initial operation of the data center can be performed; It is set as an outdoor data center.

In such a server cooling system, the efficiency of power consumption is a major problem. In the data center, since a large number of servers are used, power consumption is large, so the power consumed outside the server is preferably as small as possible. This has the advantage of being economical that can reduce the running cost and reduce the use cost seen by the user, and the environmental advantage that can suppress the power consumption.

For the power consumed by the server cooling system, an indicator called PUE (Power Usage Effectiveness) is used, which is used to obtain the power consumed by the server system as a whole (WH_RCV) relative to the power consumed by the server itself (WH_RAC). Magnification. If it is assumed that the sum of the power consumption of the cooling server and the power of the additional equipment is zero, the PUE is 1.0.

In order to reduce this PUE as much as possible, various proposals have been made. The technique disclosed in Patent Document 2 is to reduce the PUE by arranging a cooling air at a server rack by providing a corridor between a server rack and a chamber provided between the cold aisle and the hot aisle. .

In Patent Document 3, a fan that can send a larger air volume than an internal fan provided in the server and a temperature detecting device provided close to the fan are provided in the exhaust port of the server rack, and the temperature detecting device is provided by the corresponding temperature detecting device. The measured value is used to adjust the air volume of the fan to prevent ineffective air intake and to construct an energy-saving system with high air-conditioning efficiency. [Prior Technical Literature] [Patent Literature]

[Patent Document 1] Japanese Laid-Open Patent Publication No. JP-A No. Hei. No. Hei. No. Hei.

[Problem to be Solved by the Invention] In the cooling system of Patent Document 1, the cooling efficiency is determined by the flow of the cold air flowing from the cold zone to the hot zone. The flow of this cold air depends on the size of the air conditioner and the casing provided in the hot zone. However, the efficiency and size of the air conditioning unit and the housing have some limitations and cannot be completely freely designed.

For example, in the case where a housing of a certain size is not available, there is not necessarily an air conditioner that is most suitable for the size. That is, the efficiency of the cooling capacity cannot be optimized without a combination of an air conditioner and a housing that are just right.

As in the cooling system of Patent Document 2, it is desirable to achieve high efficiency. However, as the size of the server is larger, the cooling efficiency is lowered, so that power consumption is required to be reduced.

Patent Document 3 requires local air conditioning for a server that is a heat source load, and therefore requires high efficiency. However, in Patent Document 3, as the server cooling system, only the configuration in which the cooler is disposed on the side surface of the servo rack is disclosed. Therefore, the reduction effect of the power consumption converted into PUE is low. [Method of solving the problem]

The present invention has been made in view of the above problems, and is a server cooling system in which a hot channel (hot zone) and a cold aisle (cold zone) are disposed in a chamber (housing), and a server is disposed on the boundary thereof. The rack can increase the cooling efficiency (making the PUE smaller to 1.0).

More specifically, the server cooling system of the present invention divides the chamber into two parts, forming a cold channel in one part and a hot channel in another part, and configuring a servo on the boundary between the cold channel and the hot channel. The rack is characterized in that: an air conditioner is disposed on the hot channel side; a circulation passage is disposed from the air conditioner to the cold passage; and a rack fan is disposed in the heat passage of the heat generating portion of the server rack The rack fan reduces the air volume of the air conditioner, and the air volume of the rack fan is less than the reduced air volume of the air conditioner. [Effects of the Invention]

In the server cooling system of the present invention, since the server rack is disposed at the boundary between the cold aisle and the hot aisle, a fan is disposed at the exhaust port of the server rack, so that the fan bears a part of the rated air volume of the air conditioner, and therefore The same cooling capacity, but can suppress the power consumed by the server cooling, can obtain a cooling system with high cooling efficiency.

Further, in the server cooling system of the present invention, a heat pipe can also be used. Therefore, in a period in which the winter temperature is low, it is expected to achieve a cooling efficiency in which the PUE is close to 1.0.

Hereinafter, the server cooling system of the present invention will be described with reference to the drawings. However, the following description is illustrative of the embodiments of the present invention, and the present invention is not limited to the embodiments described below. The following embodiments can be modified without departing from the scope of the invention.

<Description of Configuration> Fig. 1 is a view showing the configuration of a server cooling system of the present invention. The server cooling system 1 of the present invention has a chamber 10; a circulation passage 12 disposed under the floor of the chamber 10; an external air passage 14 disposed in the ceiling space of the chamber 10; and a servo frame 20 disposed in the chamber Near the center of the chamber 10; the rack fan 32 is disposed on the back side of the server rack 20; and an air conditioner (cabinet type air conditioner) 22 is disposed on the back side of the server rack 20 in the chamber 10 (hot aisle) 10h side). Further, a humidifier 13 may be provided in the circulation passage 12, and a heat pipe 24 (the evaporator 24a of the heat pipe 24) may be disposed in the upper portion of the cabinet type air conditioner 22. Also, the heat pipe 24 is also referred to as a heat pipe auxiliary cooler 24.

In the outdoor air passage 14, a ventilating baffle 14d and a ventilation fan 14f are provided at the inlet 14a. Further, the outer air passage 14 is provided with a condenser 24b of the heat pipe 24.

Further, a control device 30 for controlling the entire body is provided outside the chamber 10. In the chamber 10, an intake air temperature sensor TSA, an intake humidity sensor HSA, a return air temperature sensor TRE, a return air humidity sensor HRE, an external air temperature sensor TOA, and an outside are provided. Gas and humidity sensor HOA, heat pipe evaporator inlet temperature sensor THP, cabinet air conditioner power monitor WHPAC, servo power monitor WHRAC, power monitor WHRCV, rack fan power monitor WHRF, heat pipe power monitoring The device WHHP is connected to the control device 30, respectively. Further, the control device 30 is also connected to the air conditioner 22, the ventilation fan 14f, and the ventilation flap 14d.

FIG. 2 shows a top view of the chamber 10. At approximately the center of the chamber 10, a server rack 20 is arranged in an array. A partition wall 16 is disposed between the server frame 20 and the side of the chamber 10. A rack fan 32 is provided on the hot aisle 10h side of the server rack 20. In the example, the air conditioner 22 is disposed on the wall side of the hot runner 10h side. Further, the heat pipe 24 is disposed on the top surface of the air conditioner 22, but is not illustrated here.

Referring again to FIG. 1, a partition wall 16 may be provided between the server frame 20 and the top plate of the chamber 10.

<Details of Configuration and Connection Relationship> Referring to Fig. 1, the chamber 10 has a rectangular parallelepiped shape covered with a heat insulating material. However, as long as the internal substance can be divided into two parts, it is not a rectangular parallelepiped shape. Here, "substantially divided into two parts" means that the inside of the chamber 10 is divided into two regions of a cold passage 10c filled with cold air and a hot passage 10h filled with heating which is warmed by heat exchange with a server. That is, as long as the cold passage 10c and the hot passage 10h can be provided, the inside of the chamber 10 can be divided into two or more. Specifically, for example, the inside of the chamber 10 can be divided into three parts, the middle of the chamber 10 can be set as the cold aisle 10c, and the space at both ends can be set as the hot aisle 10h.

Further, the partition wall 16 may not be further provided, and the cold air passage 10c and the heat passage 10h may be formed by the flow of the cold air or the warm air, and have an intermediate portion at the boundary thereof. In other words, the term "substantially divided into two parts" may also include a case where the partition wall 16 is not provided.

The server frame 20 is disposed at a boundary between the hot aisle 10h and the cold aisle 10c. The server rack 20 is a scaffold provided with a laminate which penetrates from the front surface (the cold passage 10c side) toward the rear surface (the hot passage 10h side), and has a CPU (Central Processor Unit) and a memory in the penetrating portion. The body of the server unit 20u (refer to Figure 3). A plurality of server racks 20 can be configured such that the front faces of all of the server racks 20 face the cold aisle 10c and the back faces toward the hot aisle 10h. Further, "server rack power consumption" refers to power consumed by all server units 20u.

Between the server frame 20 and the chamber 10, the side surface side and the top surface side of the servo frame 20 have a gap with the chamber 10. The person shielding this gap is a shielding mechanism. Here, the shielding mechanism is the partition wall 16. The shielding mechanism may be a method other than the partition wall 16 as long as cold air can be prevented from passing from the cold passage 10c to the hot passage 10h side.

An air conditioner (cabinet type air conditioner) 22 is disposed on the inner wall of the chamber 10 on the side of the hot aisle 10h. In the air conditioner (22), a return air intake port (22in) is provided on the front surface, and a cold air outlet (22out) is provided on the bottom surface. Moreover, the air conditioner 22 has a circulation fan 34 and a circulation fan inverter 36 for driving the circulation fan 34 in order to adjust the amount of blown air.

Therefore, the air conditioner 22 can change the blowing flow rate of the cold air in multiple stages. The server cooling system 1 of the present invention can pass the rated air supply amount of the air conditioner 22 by the rack fan 32 disposed directly behind the air conditioner 22 and the server rack 20.

This is because the air conditioner 22 must be able to adjust the amount of air supplied to less than the rated air supply amount. The adjustment of the air blowing amount of the air conditioner 22 is performed by the air conditioner 22 receiving the request instruction (cooling capability level request) C22 from the control device 30. More specifically, when the instruction signal C22 from the control device 30 is received, the adjustment is made by the change in the amount of blown air of the circulation fan 34 in the air conditioner 22. Further, although not shown, the cold air of the heat pipe 24 can be blown by the circulation fan 34 of the air conditioner 22.

Below the floor of the chamber 10, a circulation passage 12 is provided. The circulation passage 12 sends the cold air from the cold air outlet 22out of the air conditioner 22 to the transfer passage of the cold air supply port 10ct of the cold aisle 10c. Therefore, a through hole is provided on the hot channel 10h side and the cold channel 10c side of the floor surface of the chamber 10.

The through hole on the side of the hot aisle 10h sends cold air from the air conditioner 22 to the circulation passage 12, and the through hole on the side of the cold passage 10c sends the sent cold air into the chamber 10. The through hole on the side of the cold aisle 10c is referred to as a cold air supply port 10ct. In order to prevent the falling of the circulation passage 12, it is preferable to arrange a grill or the like on the cold air supply port 10ct.

Further, in the circulation passage 12, a cold air baffle 38 is provided between the cold air outlet 22out and the cold air supply port 10ct. In the server cooling system 1 of the present invention, the supply of cold air from the air conditioner 22 is suppressed, and the amount of air in the suppressed portion is compensated by the gantry fan 32, whereby the overall power consumption is suppressed.

When the circulation fan 34 of the air conditioner 22 regulates the supply of the cold air by the circulation fan inverter 36, the cold air baffle 38 is not required. However, when the circulation fan 34 of the air conditioner 22 does not include the circulation fan inverter 36, the cold air damper 38 is used to reduce the air blow of the cold air from the air conditioner 22, compared to the case where the circulating fan inverter 36 is provided. The time is small, but the power consumption of the computer center as a whole can be suppressed.

The humidifier 13 may be disposed on the cold passage 10c side of the cold air supply port 10ct or on the side of the circulation passage 12. The humidifier 13 is for imparting humidity to the cold air (intake). If the cold air is excessively dried, static electricity is generated in the servo rack 20, which may damage the electronic machine. The humidifier 13 is configured to avoid such a state. Further, the humidifier 13 is controlled by the instruction signal C13 from the control device 30.

Here, the case where the circulation passage 12 is disposed under the floor is exemplified here, but the circulation passage 12 may not be disposed on the floor as long as the cold air from the air conditioner 22 disposed in the hot aisle 10h can be transferred to the cold passage 10c. under.

An outer air passage 14 is provided in the ceiling space of the chamber 10. The outdoor air passage 14 is provided with a passage for the air other than the ventilation fan 14f, and is a duct having an inlet 14a and an outlet 14b. In Fig. 1, an example in which the ventilation fan 14f is provided on the side of the inlet 14a is shown. The outlet 14b is also open to the outside air.

The ventilation fan 14f is connected to the control device 30. The cold air baffle 38 can also be coupled to the control unit 30 when the cold air baffle 38 is provided. In this manner, the operation can be performed in accordance with an instruction from the control device 30. The control device 30 can control by transmitting the instruction signal C14f to the ventilation fan 14f, and can control the cold air damper 38 by transmitting the instruction signal C38.

A heat pipe 24 is disposed at an upper portion of the cabinet type air conditioner 22. The heat pipe 24 uses the evaporator 24a to evaporate the solvent. The vaporized solvent is moved to the condenser 24b through the cooling conduit 24c. The condenser 24b liquefies the solvent. When the solvent is liquefied, the heat of the latent heat portion is released. The liquefied solvent is returned to the evaporator 24a by gravity through the cooling duct 24c. The heat pipe 24 is efficient because it does not use a compressor. However, its performance is affected by outside air temperature.

Further, the condenser 24b is disposed in the outdoor air passage 14. This is because the condenser 24b is preferably above the gravity of the evaporator 24a disposed on the heat pipe 24 configuration. The condenser 24b has a fan and a radiator, and is liquefied by cooling the vaporized medium.

The control device 30 is a computer composed of a CPU (Central Processing Unit) and a memory. It is preferable to have a human-machine device (interface) 30 m such as a display screen and an input device to easily monitor the state of the server cooling system 1. Further, the control device 30 is connected to each of the sensors provided in the server cooling system 1.

An intake air temperature sensor TSA and an intake air humidity sensor HSA are provided on the front surface of the server rack 20 (between the cold air supply port 10ct and the server rack 20). The signals from the sensors are set to the intake dry bulb temperature TdbSA and the intake relative humidity RHSA, and are sent to the control device 30.

Further, a return air temperature sensor TRE and a return air humidity sensor HRE are provided in front of the return air intake port 22in of the air conditioner 22 (between the return air intake port 22in and the servo chassis 20). These signals are set to the return air dry bulb temperature TdbRE and the return air relative humidity RHRE, and are transmitted to the control device 30.

Further, an outside air temperature sensor TOA and an external air humidity sensor HOA are provided at the inlet 14a of the outdoor air passage 14. These signals are transmitted to the control device 30 by the outside air dry bulb temperature TdbOA and the outside air relative humidity RHOA.

Further, a heat pipe evaporator inlet temperature sensor THP is disposed at the inlet of the evaporator 24a of the heat pipe 24. The temperature of the cold air of the heat pipe 24 can be confirmed by the intake air temperature sensor TSA. These signals are transmitted to the control device 30 at the evaporator inlet temperature TdbEV.

Further, a cabinet type air conditioner power monitor WHHPAC is disposed on the power wiring of the air conditioner 22, a heat pipe power monitor WHHP is disposed on the power wiring of the heat pipe 24, and a server is disposed on the power wiring of the server. The power monitor WHRAC is provided with a power receiving power monitor WHRCV that monitors all of the received power including the server cooling system 1 and the server. These signals are transmitted to the control device 30 as the cabinet air conditioner power consumption WH_PAC, the heat pipe power consumption WH_HP, the server rack power consumption WH_RAC, and the power receiving power WH_RCV. Further, the control device 30 is also connected to the humidifier 13 to control the operation of the humidifier 13. These sensors and signals are exemplified in Figure 1.

Figure 3 is a diagram of the server frame 20 viewed from the back. Further, the rack fan 32 is disposed on the rear surface of the server rack 20, but is omitted in this drawing. The compartment partition 16 is disposed adjacent to the server rack 20. Further, the partition wall 16 is also disposed above the server rack 20.

In the server rack 20, a plurality of server units 20u are arranged in the longitudinal direction. In the drawings, only one column is described in the vertical direction for the sake of illustration. One servo unit 20u is composed of a central portion 20c on which a CPU is mounted and a peripheral portion 20p on which peripheral devices are disposed. In the server unit 20u, the central portion 20c and the peripheral portion 20p are not heated at the same temperature, and the central portion 20c is the highest temperature, and the peripheral portion 20p does not generate heat to such an extent.

When cold air (intake air) is supplied from the side of the cold aisle 10c, heat exchange is performed in the servo rack 20, and cold air (return air) whose temperature becomes high is discharged to the side of the hot aisle 10h. The server cooling system 1 basically cools the server rack 20 in this manner.

When the cold air (intake air) flows from the cold aisle 10c to the hot aisle 10h at the same wind speed, the intake air passing through the central portion 20c rises due to heat exchange. However, the cold air (intake air) passing through the peripheral portion 20p directly passes through the servo rack 20 without the temperature rising. That is, the heat exchange efficiency with respect to the intake air becomes low. In Fig. 3, the portion of the return air having a high temperature is referred to as a symbol 21h, and the portion where the return air temperature is maintained as cold air is referred to as a symbol 21b.

4 is a plan view of the servo chassis 20 for explaining the above state. If the intake air velocity of the cold air from the cold aisle 10c is uniform throughout the server frame 20, the heat exchange is performed only at the central portion 20c. As a result, the temperature of the cold air passing through the peripheral portion 20p does not rise, and the return air temperature on the hot passage 10h side does not become high as a whole. That is, the heat exchange efficiency is low.

In the air conditioner 22, even if the return air temperature changes somewhat, the electric power consumed to reduce the return air temperature to a predetermined temperature hardly changes. Therefore, when the return air temperature is low, the overall efficiency of the server cooling system 1 is lowered.

On the other hand, the intake air velocity of the cold air from the cold aisle 10c to the hot aisle 10h is also lowered, and the heat generated by the servo unit 20u cannot be sufficiently cooled.

Therefore, in order to increase the return air temperature on the hot runner 10h side, in the server cooling system 1 of the present invention, the machine is disposed directly behind the hottest central portion 20c on the back surface of the servo rack 20 (the hot passage 10h side). Fan 32. In this way, the amount of air blown by the air conditioner 22 is reduced, and the portion of the air blow amount that is reduced is compensated by the rack fan 32. Fig. 5 is a view of the back side of the servo rack 20 as seen from the side of the hot aisle 10h. A rack fan 32 is provided directly behind the center portion 20c. Here, an example in which two rows of five-row rack fans 32 are arranged in the center portion 20c is shown.

By providing the gantry fan 32, even if the amount of air blown by the air conditioner 22 is reduced, the amount of cold air passing through the peripheral portion 20p can be reduced while maintaining the air volume passing through the heat generating central portion 20c. In this way, the temperature of the cold air on the side of the hot aisle 10h can be increased. By returning the cold air that has become high temperature to the air conditioner 22, the heat conversion efficiency of the air conditioner 22 can be improved.

Figure 6 is a top plan view of the servo chassis 20 used to display this pattern. The amount of air on the intake side is made smaller than in the case of FIG. Next, the frame fan 32 concentrates the cold air through the heat generating central portion 20c. The passing air volume of the peripheral portion 20p is reduced, and the amount of return air passing through the central portion 20c is increased. In other words, the amount of cold airflow passing through the server rack 20 is distributed.

Referring again to FIG. 1, the amount of air blown by the air conditioner 22 can be adjusted by driving the circulation fan 34 with the circulating fan inverter 36. Further, the rack fan 32 can also vary the amount of suction depending on an instruction from the control device 30. The control device 30 can monitor the temperature and humidity state of the return air according to the return air temperature sensor TRE and the return air humidity sensor HRE. Therefore, the air volume of the circulation fan 34 and the gantry fan 32 is adjusted in accordance with the temperature and humidity state of the return air.

If the rack fan 32 is driven, power consumption is generated. However, since the amount of cold air passing through the peripheral portion 20p is reduced, the reduction in power consumption due to the decrease in the air blowing amount of the air conditioner 22 can be made much larger than the total power consumption of the rack fan 32, and the power consumption of the entire cooling system can be made. decline. In other words, by reducing the air volume of the circulation fan 34 of the local exhaust and air-conditioning apparatus 22 by the rack fan 32 using the high-efficiency fan, the power consumption of the circulation fan 34, that is, the power consumption of the circulation fan 34 can be greatly reduced.

Hereinafter, the operation of the server cooling system 1 will be briefly described. The control device 30 causes the air conditioner 22 to operate only by a specific amount of the rated air volume. Now, the specific amount is set to X%. That is, the air conditioner 22 operates at a reduced X% of the rated air volume. In addition, the "rated air volume" refers to the air volume of the air conditioner 22 required to cool the heat generation amount obtained from the power consumed by the server rack 20 to be cooled. Moreover, this X% is used to cool the overall air volume of the server rack 20.

Next, the control device 30 operates the gantry fan 32 to cause the gantry fan 32 to send a portion of the reduced portion of the air volume. That is, since the rack fan 32 is provided directly behind the center portion 20c, it is not necessary to cool the entire air volume of the server rack 20, but only the air volume of the central portion 20c needs to be cooled, and the reduced air volume can be utilized. Part of it is cooled. Further, it is preferable that the drive portion of the rack fan 32 is configured to be variably operated to some extent. For example, for DC control or inverter control, it can be used as a high-efficiency fan to reduce power consumption.

In this manner, by controlling the air volume of the air conditioner 22 and the air volume of the gantry fan 32 to be the rated air volume of the air conditioner 22, the power design of the entire cooling system is performed, and after the rated air volume of the air conditioner 22 is obtained, the rack is introduced into the rack. The fan 32 can reduce power consumption.

Further, the control device 30 measures the outside air temperature by the outside air temperature sensor TOA, and the outside air humidity sensor HOA measures the outside air humidity, and determines the amount of reduction of the air conditioner 22 corresponding to the current outside temperature and humidity, or switches the operation to be introduced. Heat pipe 24 of the secondary cooling device. In particular, if the heat pipe 24 is combined with the frame fan 32 as a local cooling fan, a very high cooling efficiency can be obtained.

Further, the reduction in the amount of air blown from the air conditioner 22 can be performed not only by reducing the operation of the air conditioner 22 but also by the cold air baffle 38 provided in the circulation passage 12. This is because the reduction in air supply volume itself can reduce the PUE.

Hereinafter, the air conditioner 22 serving as the main cooling device is combined with the heat pipe 24 serving as the sub-cooling device and the frame fan 32 serving as the partial cooler, and the power consumption is calculated in comparison with the case where only the main sub-cooling device is used for cooling. The degree of improvement and the results are shown.

<System Configuration> A system with the following specifications is assumed.

a) Set the computer center to the container type data center (full channel cover). Further, the full channel cover is a method in which the channel 10c and the heat channel 10h are completely separated by the partition wall 16 or the like.

b) Set the server rack 20 to four. It is assumed that 37 1U type servers (250 [W]) and 2 1U type HUBs (100 [W]) are housed in each server rack. The total power consumption per servo rack is 9.45 [kW]. If the number of the server racks 20 is four, the power consumption of the server is 9.45 [kW] × 4 racks = 37.8 [kW].

c) Prepare one main cooling unit (cabinet type air conditioner 22). The specifications are as follows. The cooling capacity: 40 [kW], the operating coefficient COP is set to 2.5 at an outside air temperature of 35 ° C, and is set to 3.5 at an outside air temperature of 10 ° C. The cabinet type air conditioner 22 consumes 36.3 [kW] of electric power by the compressor.

Further, the heat pipe auxiliary cooler 24 was stopped at an outdoor air temperature of 35 ° C, and the COP was set to 30 at an outdoor air temperature of 10 ° C. The power consumption of the heat pipe 24 is set to consume 1.4 kW. This operation switching system control device 30 is performed based on the outside air temperature and humidity measured by the outside air temperature sensor TOA and the outside air humidity sensor HOA.

The air conditioner of the cabinet air conditioner 22 is sent to the circulation fan 34 of the cold aisle 10c, and a multi-blade air blower is used. The air blowing capability of the multi-blade air blower was set to 12,000 [m ³ /h], the power consumption was 3.7 [kW], and the external static pressure was set to 100 Pa.

d) Prepare 80 rack fans 32. The rack fan 32 uses an axial fan. The axial fan has a blowing capacity of 150 m ³ /h. The fan diameter is φ145 mm, and the box area through which the wind passes is 200×200 mm ² . The motor power consumption was set to 4 W, and the number of rotations was set to 2000 r/min.

Each of the two server racks is configured with two sets of 10 units. The total air supply amount of the 80 rack fans 32 is 150 [m ³ /h] × 2 side by side × 10 layers × 4 racks = 12,000 [m ³ /h]. Further, 80 rack fans 32 correspond to the air volume of the circulation fan 34.

Further, COP is an action coefficient and is basically obtained as follows.

The air volume qts passing through the cooler is obtained by qts = v × S [m ³ ]. Here, v is the wind speed passing through the cooler, and S is the sectional area through which the cooler cool air passes. When the average temperature of the return air supplied to the cooler is T1, the average temperature of the outlet temperature of the cooler is T2, the power consumption of the cooler is WH_TS, and the air density is 1.293 [kg/m ³ ], the cooling treatment heat Q of the cooler is: Q = 1.293 × qts × (T1 - T2) [KJ]. The calculation of the action coefficient COP is: COP=Q/WH_TS.

Next, set the following conditions. The fan air volume is proportional to the motor speed N, and the pressure P is proportional to the second power N ^{2 of the} motor speed, and the fan shaft power is proportional to the third power N ^{3 of the} rotational speed.

Refer to Figure 7. Fig. 7 is a characteristic hypothesis diagram of the main cooling circulating fan 34. The horizontal axis is the air volume (m ³ /h), and the vertical axis is the static pressure (Pa). LINE1 is the air volume-static pressure curve at the maximum air volume; LINE2 is the air volume-static pressure curve when the air volume is about half. The operating point can be obtained as the intersection of the system impedance (LINE3) when the circulating fan inverter 36 is used and these curves. That is, if the air volume is changed, the operating point moves on the impedance of the system.

Further, although the cold air baffle 38 can be used, compared with the LINE3 of the system impedance of the circulating fan inverter 36 of Fig. 7, it is a curve having a large inclination close to the vertical axis, so that it is impossible to obtain a high frequency like a frequency converter. The effect of efficiency.

When the air volume is set to 1/2 from the rated operating point A of the circulating fan 34 of the main cooling device (air-conditioning device 22) of the inverter to the operating point B, the power consumption is 1/8. Power consumption of operating point (A) 3.7 [kW] → power consumption of operating point (B) 463 [W] ・・(1) From the operating point A to the operating point B, the air volume is reduced by the inverter, and the reduced portion is reduced. It is compensated by the rack fan 32. That is, if the rated air volume of the circulation fan 34 is 12,000 [m ³ /h], the gantry fan 32 compensates for 1/2, that is, 6,000 [m ³ /h].

More specifically, assuming that the air volume per one rack fan 32 is 75 [m ³ /h], the air volume of all the rack fans of the four server racks is obtained as in the equation (2). 75 [m ³ /h] × 2 in parallel × 10 layers × 4 racks = 6,000 [m ³ /h] ・ (2) Local ventilation is performed by using all the rack fan air volumes of the above formula (2).

The power consumption of the rack fan 32 corresponding to the above is obtained by the equation (3). 2.4 [W] × 2 in parallel × 10 layers × 4 racks = 192 [W] ・ (3) From the total value of the equations (1) and (2), the sum of the fan power consumption is 655 [W] ・・(4) On the other hand, when it is only circulated by the circulation fan 34, it is 3.7 [kW] ・・(5)

As described above, when the 1/2 air volume of the circulation fan 34 of the air-conditioning apparatus 22 is compensated by the gantry fan 32, the reduction of the transmission power of the entire circulation fan 34 is obtained by the following equations (4) and (5). (6) Seek.

(3700-655)/3700×100=82.2% ・ (6) From the equation (6), it is possible to reduce the total electric power transmitted by the circulating fan 34 by 82.6%.

This is compared by PUE. Since the PUE is affected by the temperature of the outside air, the situation is distinguished as follows.

a) The PUE when the circulation fan 34 performs the cyclic transportation only in the summer is obtained as shown in the formula (7). PUE=(16300+3700+37800)/37800=1.53 ・・(7)

b) The PUE when the rack fan 32 compensates for the 1/2 air volume of the circulation fan 34 of the air conditioner 22 in the summer is obtained as shown in the equation (8). PUE=(16300+655+37800)/37800=1.45 ・・・(8)

c) The PUE at the time of circulating transportation by the circulation fan 34 of the air conditioner 22 in winter is obtained as shown in the formula (9). The COP of the air conditioning unit 22 in winter was raised from 2.5 to 3.5 as compared with the summer season. PUE=(11643+3700+37800)/37800=1.4 ・・・・(9)

d) The PUE when the gantry fan 32 compensates for the 1/2 air volume of the circulation fan 34 of the air-conditioning apparatus 22 in winter is obtained as shown in the formula (10). PUE=(11643+655+37800)/37800=1.33 ・・・・(10)

e) The PUE when the heat pipe auxiliary cooler 24 is operated in winter is obtained as shown in the formula (11). The compressor of the air conditioner 22 can be completely stopped at an outside air temperature of 10 °C. PUE=(3700+37800)/37800=1.1 ・・・・・・・・・(11)

f) In the winter, the heat pipe auxiliary cooler 24 is operated, and the PUE when the gantry fan 32 compensates for the 1/2 air volume of the air conditioner 22 is obtained as shown in the formula (12). PUE=(662+37800)/37800=1.02 ・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・A highly efficient server cooling system with a PUE of 1.02 is achievable.

Thus, by combining the air conditioner 22 or the heat pipe auxiliary cooler 24 with the gantry fan 32, the PUE can be greatly improved. In practice, the ratio of the air volume of the air conditioning unit 22 or the heat pipe auxiliary cooler 24 to the rack fan 32 must be carefully adjusted depending on the size of the chamber 10 and the size of the server rack 20. Therefore, the ratio of the air volume of the rack fan 32 is not particularly limited.

However, by setting the air volume of the air conditioner 22 or the heat pipe auxiliary cooler 24 and the gantry fan 32 to 1/2, in most of the server systems, only by the air conditioner 22 or the heat pipe type When the cooler 24 is in progress, a more efficient cooling can be achieved.

As described above, according to the server cooling system 1 of the present invention, the following effects can be achieved.

(1) A rack fan 32 is provided in the server machine as a partial dispersion, and a part of the circulation fan 34 as the main cooling cabinet type air conditioner 22 is used to remove power from the space in the data center. The recirculation of the 10h side to the cold aisle 10c side and the inefficiently transmitted power due to the reverse air supply from the gap of the servo rack 20 can reduce the transportation power of the cold air as a whole.

(2) By supplying the ventilation power corresponding to the servo load (electric power) by the gantry fan 32, the ventilation power of the cooling server unit 20u can be reduced. If the size of the server is larger, that is, the more the number of the server racks 20, the greater the effect of (1) (2).

(3) By using the partial ventilation of the gantry fan 32, the high-temperature heat-generating region of the CPU central portion 20c on the back surface of the servo rack 20 is ventilated, and the ineffective ventilating of the low-temperature heating region of the peripheral portion 20p can be reduced. power.

(4) By returning the exhaust gas which is uniform and high temperature from the back of the servo rack 20 to the cabinet air conditioner 22 as a whole, it is possible to efficiently raise the heat exchanger auxiliary cooler 24 when the return air path is provided. The cooling capacity of the machine. [Industry use possibility]

The invention is applicable to a server cooling system in a computer center.

1‧‧‧Server Cooling System
10‧‧‧ chamber
10c‧‧‧cold passage
10ct‧‧‧air supply port
10h‧‧‧ hot aisle
12‧‧‧Circular passage
13‧‧‧Humidifier
14‧‧‧ outside air passage
14a‧‧‧ Entrance
14b‧‧‧Export
14d‧‧‧Ventilation baffle
14f‧‧‧ ventilation fan
16‧‧‧ next door (shading mechanism)
20‧‧‧Server Rack
20c‧‧‧Central Department
20p‧‧‧ peripherals
20u‧‧‧server unit
21b‧‧‧ Maintain the return air section
21h‧‧‧Return part of high temperature
22‧‧‧Air conditioning unit (cabinet type air conditioner)
22in‧‧‧ return air inlet
22out‧‧‧Air air blowout
24‧‧‧ Heat pipe (heat pipe auxiliary cooler)
24a‧‧‧Evaporator
24b‧‧‧Condenser
24c‧‧‧Cooling catheter
30‧‧‧Control device
30m‧‧‧human machine
32‧‧‧Rack fan
34‧‧‧Circular fan
36‧‧‧Circular fan inverter
38‧‧‧Air shield
C13‧‧‧ indication signal
C14d‧‧‧ indication signal
C14f‧‧‧ indication signal
C22‧‧‧ indication signal
C24‧‧‧ indication signal
C38‧‧‧ indication signal
TSA‧‧‧Intake Temperature Sensor
HSA‧‧‧Intake Humidity Sensor
TRE‧‧‧ return air temperature sensor
HRE‧‧‧Return humidity sensor
TOA‧‧‧ outside air temperature sensor
HOA‧‧‧Outdoor humidity sensor
WHPAC‧‧‧ cabinet air conditioner power monitor
WHHP‧‧‧heat pipe power monitor
WHRAC‧‧‧Server Power Monitor
WHRCV‧‧‧Powered Power Monitor
WHRF‧‧‧Rack Fan Power Monitor
THP‧‧‧heat pipe evaporator inlet temperature sensor

FIG. 1 is a configuration diagram of a server cooling system 1. 2 is a plan view of a chamber of the server cooling system 1. [Fig. 3] A view seen from the back of the servo rack. Fig. 4 is a plan view of the servo rack showing an air flow diagram when the thermal efficiency is poor. [Fig. 5] A view seen from the back of the servo rack. Fig. 6 is a plan view of the servo rack showing an air flow diagram when the thermal efficiency is high. Fig. 7 is a characteristic diagram of a circulation fan of an air conditioner.

1‧‧‧Server Cooling System

10‧‧‧ chamber

10c‧‧‧cold passage

10ct‧‧‧air supply port

10h‧‧‧ hot aisle

12‧‧‧Circular passage

13‧‧‧Humidifier

14‧‧‧ outside air passage

14a‧‧‧ Entrance

14b‧‧‧Export

14d‧‧‧Ventilation baffle

14f‧‧‧ ventilation fan

16‧‧‧ next door (shading mechanism)

20‧‧‧Server Rack

22‧‧‧Air conditioning unit (cabinet type air conditioner)

22in‧‧‧ return air inlet

22out‧‧‧Air air blowout

24‧‧‧ Heat pipe (heat pipe auxiliary cooler)

24a‧‧‧Evaporator

24b‧‧‧Condenser

24c‧‧‧Cooling catheter

30‧‧‧Control device

30m‧‧‧human machine

32‧‧‧Rack fan

34‧‧‧Circular fan

36‧‧‧Circular fan inverter

38‧‧‧Air shield

C13‧‧‧ indication signal

C14d‧‧‧ indication signal

C14f‧‧‧ indication signal

C22‧‧‧ indication signal

C24‧‧‧ indication signal

C38‧‧‧ indication signal

TSA‧‧‧Intake Temperature Sensor

HSA‧‧‧Intake Humidity Sensor

TRE‧‧‧ return air temperature sensor

HRE‧‧‧Return humidity sensor

TOA‧‧‧ outside air temperature sensor

HOA‧‧‧Outdoor humidity sensor

WHPAC‧‧‧ cabinet air conditioner power monitor

WHHP‧‧‧heat pipe power monitor

WHRAC‧‧‧Server Power Monitor

WHRCV‧‧‧Powered Power Monitor

WHRF‧‧‧Rack Fan Power Monitor

THP‧‧‧heat pipe evaporator inlet temperature sensor

Claims (6)

A server cooling system divides a chamber into two parts, forming a cold channel in one part and a hot channel in another part, and configuring a server rack on a boundary between the cold channel and the hot channel, wherein Having: an air conditioning device disposed on the hot aisle side; a circulation passage from the air conditioning device to the cold aisle; and a rack fan disposed on a hot runner surface of the heat generating portion of the server rack, the rack fan making The air volume of the air conditioner is reduced, and the air volume of the rack fan is equal to or less than the air volume of the air conditioner. A server cooling system divides a chamber into two parts, forming a cold channel in one part and a hot channel in another part, and configuring a server rack on a boundary between the cold channel and the hot channel, wherein Having: an air conditioning device disposed on the hot aisle side; a circulation passage from the air conditioning device to the cold aisle; and a rack fan disposed on a hot runner surface of the heat generating portion of the server rack, the rack fan The amount of cold air flow through the server rack has a distribution. The server cooling system of claim 1 or 2, wherein the heat pipe side is provided with a heat pipe. The server cooling system of claim 1 or 2, wherein the air volume of the rack fan is changeable in accordance with power consumption of the heat generating portion of the server rack. The server cooling system of claim 1 or 2, wherein the circulating fan of the air conditioning device controls the air volume by using a frequency converter. The server cooling system of claim 1 or 2, wherein the server cooling system is disposed between the server frame and the inner wall of the chamber.