AU2021398579A1

AU2021398579A1 - Cooling device and control method for cooling device

Info

Publication number: AU2021398579A1
Application number: AU2021398579A
Authority: AU
Inventors: Masaki Chiba; Mahiro HACHIYA; Yoshinori Miyamoto; Takashi Ohtsuka; Koichi Todoroki; Minoru Yoshikawa
Original assignee: NEC Corp
Current assignee: NEC Corp
Priority date: 2021-09-13
Filing date: 2021-09-13
Publication date: 2023-03-30
Also published as: WO2023037543A1; JPWO2023037543A1; JP2023041593A; US20230213253A1; JP7056814B1; EP4174402A1

Abstract

An object of the present invention is to prevent cavitation in a refrigerant pump from occurring due to a decrease in a net positive suction head in a cooling device. A cooling device of the present invention is a cooling device using a refrigeration cycle in which a refrigerant is circulated through a heat receiver (1), a compressor (2), a heat radiator (3), and an expander (4), and includes a tank (5) that separates the refrigerant supplied from the expander (4) into a gas phase refrigerant and a liquid phase refrigerant, a pump (6) that sends the liquid phase refrigerant separated in the tank (5) to the heat receiver (1), and a control unit (7) that controls the amount of increase in pressure of the compressor (2) in the refrigeration cycle, and the control unit (7) activates the pump (6) on condition that a value of a net positive suction head of the pump (6) exceeds a predetermined threshold value.

Description

DESCRIPTION TITLE OF INVENTION: COOLING DEVICE AND CONTROL METHOD FOR COOLING DEVICE TECHNICAL FIELD

[0001]

The present invention relates to a cooling device and a control method therefor.

In particular, the present invention relates to a cooling device using a refrigeration cycle

suitable for air conditioning equipment in a data center and a control method therefor.

BACKGROUND ART

[0002]

A cooling device using a refrigeration cycle for radiating heat to an atmosphere

via a refrigerant that has received heat from heat generation sources through steps of

heat-receiving, compressing, heat-radiating, and expanding a refrigerant is used to cool a

space in which a large number of the heat generation sources such as electronic devices

are housed, such as a server room in a data center.

In this refrigeration cycle, because the refrigerant repeats the phase change

between a liquid phase and a gas phase in each step of the cycle, it is necessary to

achieve an efficient operation of the refrigeration cycle by appropriately maintaining a

phase state of the refrigerant in pipelines between the respective steps.

[0003]

For example, in the refrigerant circulation system, because a compressor that

sucks a refrigerant in a gas-liquid mixed phase state of which heat has been received by a heat receiver and increases a pressure at a predetermined compression ratio has a structure based on compression of a gas phase refrigerant, it is not possible to compress a liquid phase refrigerant. Therefore, before the refrigerant is sucked into the compressor, it is necessary to separate the refrigerant in the mixed phase state into gas and liquid phase refrigerants by temporarily storing the refrigerant in a gas-liquid separation tank

(generally, also serving as a tank that separates a gas phase refrigerant from a gas-liquid

mixed phase refrigerant directed to the heat receiver and stores a liquid phase refrigerant

at a predetermined level).

On the other hand, switching from conventional high-pressure hydro fluoro

carbons (HFCs: high-pressure HFCs) having a difference between an evaporation

pressure and a condensation pressure on the order of 1000 kPa to low-pressure hydro

fluoro olefins (low-pressure HFOs) having a difference between an evaporation pressure

and a condensation pressure of about 100 kPa and a maximum vapor pressure of 1000

kPa or less, as a refrigerant that is used in the refrigeration cycle, is expected in

consideration of an environmental load in recent years.

[0004]

In the refrigeration cycle using the low-pressure refrigerant, because it is

necessary to appropriately perform gas-liquid separation in each step of the heat

reception side and the heat radiation side of the refrigerant circulation system, for

example, a tank (gas-liquid separator) having a predetermined capacity is provided for

the purpose of gas-liquid separation on the inlet side of the compressor and gas-liquid

separation on the suction side of a pump that sends the refrigerant to the heat receiver.

[Prior Art Documents]

[Patent Documents]

[0005]

[Patent Document 1] Japanese Unexamined Patent Application, First Publication No.

2016-205773

[Patent Document 2] Japanese Unexamined Patent Application, First Publication No.

2010-243095

SUMMARY OF THE INVENTION

Problem to be Solved by the Invention

[0006]

However, in a case in which the tank is connected to a suction side of the

compressor, when a pressure in the tank decreases with the suction of the compressor, the

pressure drops below a saturated vapor pressure of a low-pressure refrigerant stored in

the tank, and cavitation may occur in the liquid phase refrigerant sucked into a pump for

sending the liquid phase refrigerant from the tank to the heat receiver. Further, because

the saturated vapor pressure on a saturated vapor pressure curve becomes high when the

temperature of the refrigerant is high, such as when a refrigeration cycle is activated, the

risk of cavitation occurrence tends to increase.

When the cavitation occurs due to such a cause, a decrease in flow rate of the

refrigerant to be sent from the pump is caused, the liquid phase refrigerant having a

sufficient flow rate cannot be supplied to the heat receiver, and it becomes difficult to

maintain cooling air supplied from the cooling device to a cooling target below a

predetermined temperature.

Because this tendency of cavitation occurrence is more significant when a

low-pressure refrigerant is used, it is required to pay close attention to an operation of the

pump in order to maintain an appropriate cooling capacity.

[0007]

Patent Document 1 related to the present application describes a pump provided

in a refrigeration cycle to supply a refrigerant, but because the cycle is a cycle in which

the refrigerant is supplied to a heat receiver via a path including heat radiator - tank

pump - expansion valve, Patent Document 1 cannot be immediately applied to prevention

of cavitation in the refrigeration cycle using the low-pressure refrigerant having the

above-described characteristics.

[0008]

Patent Document 2 related to the present application discloses a technology

regarding a vortex type refrigerant liquid pump having a gas-liquid separator built

thereinto, but does not disclose a technology for preventing cavitation of a refrigerant in a

pump that pumps a low-pressure refrigerant having the above-described characteristics.

[0009]

An object of the present invention is to prevent cavitation from occurring in a

pump that is used for pumping of a liquid phase refrigerant in a refrigeration cycle in

which cooling is performed through circulation of the refrigerant.

Means for Solving the Problem

[0010]

In order to solve the above problem, a first example aspect of the present

invention proposes the following means.

A cooling device according to the first example aspect of the present invention is

a cooling device using a refrigeration cycle in which a refrigerant is circulated through a

heat receiver, a compressor, a heat radiator, and an expansion valve, the cooling device

including: a gas-liquid separator configured to perform gas-liquid separation on the

refrigerant supplied from the expansion valve, a pump configured to send a liquid phase refrigerant separated by the gas-liquid separator to the heat receiver, and a control unit configured to control opening and closing of a refrigerant flow path of the refrigeration cycle, and an operation and stopping of the compressor and the pump, wherein the control unit controls the operation and stopping of the pump, and starts the operation of the pump on condition that a net positive suction head of the pump has reached a predetermined value or more.

[0011]

A second example aspect of the present invention also proposes the following

means.

A control method for a cooling device according to the second example aspect of

the present invention is a control method for a cooling device using a refrigeration cycle

in which a refrigerant is circulated through a heat receiver, a compressor, a heat radiator,

and an expander, the control method including: controlling, by a control unit, an

operation and stop of a pump; and starting, by a control unit, the operation of the pump

on condition that a net positive suction head of the pump has reached a predetermined

value or more.

Effect of the Invention

[0012]

In the present invention, it is possible to allow the refrigerant to have an

appropriate phase of a gas phase and a liquid phase at various places constituting the

refrigeration cycle.

BRIEF DESCRIPTION OF THE DRAWINGS

[0013]

Fig. 1 is a piping system diagram of a cooling device according to a minimum

configuration example of the present invention.

Fig. 2 is a process diagram of a control method for a cooling device according to

the minimum configuration example of the present invention.

Fig. 3 is a flowchart of an operation of a control unit of a cooling device

according to a first embodiment of the present invention.

Fig. 4 is a piping system diagram illustrating an overall configuration of the

cooling device according to the first embodiment of the present invention.

Fig. 5 is a piping system diagram illustrating an overall configuration of a

cooling device according to a second embodiment of the present invention.

Fig. 6 is a flowchart of an operation of a control unit of a cooling device

according to a third embodiment of the present invention.

Fig. 7 is a piping system diagram illustrating an overall configuration of the

cooling device according to the third embodiment of the present invention.

Fig. 8 is a flowchart of an operation of a control unit of a cooling device

according to a fourth embodiment of the present invention.

Fig. 9 is a piping system diagram illustrating an overall configuration of the

cooling device according to the fourth embodiment of the present invention.

EXAMPLE EMBODIMENTS

[0014]

A configuration of a cooling device according to a minimum configuration of

the present invention will be described with reference to Fig. 1. This cooling device is a

cooling device using a refrigeration cycle in which a refrigerant is circulated through a

heat receiver 1, a compressor 2, a heat radiator 3, and an expander 4, and includes a tank that separates the refrigerant supplied from the expander 4 into a gas phase refrigerant and a liquid phase refrigerant, a pump 6 that sends the liquid phase refrigerant separated in the tank 5 to the heat receiver 1, and a control unit 7 that controls the amount of increase in pressure of the compressor 2 in the refrigeration cycle, in which the control unit 7 controls the operation and stop of the pump 6, and starts the operation of the pump on condition that a net positive suction head of the pump 6 has reached a predetermined value or more. That is, the compressor 2 is operated to decrease a temperature of the refrigerant flowing through a heat radiator side loop (a refrigerant circulation loop) indicated by an arrow A in Fig. 1, and then, the refrigerant is caused to flow through a heat receiver side loop (a refrigerant circulation loop) indicated by an arrow B in Fig. 1 on condition that the net positive suction head has reached a predetermined value or more.

[0015]

According to the above configuration, because the pump 6 is activated by the

control unit 7 on condition that a pressure determined according to the net positive

suction head of the refrigerant sucked into the pump 6, that is, a pressure determined

according to a pressure measurement value of a refrigerant liquid (a liquid phase

refrigerant) separated in the tank 5 and sucked into the pump 6, a head difference from a

liquid level in the tank 5 to the pump 6 (a pressure generated by a density of the

refrigerant liquid at a temperature at that point in time and gravity due to a difference in

height), and a saturated vapor pressure of the refrigerant in the tank 5 is equal to or

higher than a predetermined pressure, it is possible to maintain smooth circulation of the

refrigerant in the cooling cycle without causing cavitation in the refrigerant liquid to be

sucked.

[0016]

An example of a calculation equation using parameters actually measured in the

control of the control unit 7 includes Equation (1) below.

Net positive suction head = (pump inlet pressure - saturated vapor

pressure)/(density of refrigerant liquid x gravitational acceleration) -- (1)

In a temperature range in which the present invention is implemented, because

change in the density of the refrigerant liquid is negligibly small, the density can be

treated as a constant in terms of control.

[0017]

A control method for a cooling device according to the minimum configuration

of the present invention will be described with reference to Fig. 2. This control method

for a cooling device is a control method for a cooling device using a refrigeration cycle in

which a refrigerant is circulated through the heat receiver 1, the compressor 2, the heat

radiator 3, and the expander 4, and the control unit 7 controls an operation and stop of the

pump 6 and starts the operation of the pump 6 on condition that the net positive suction

head of the pump 6 has reached a predetermined value or more. That is, the cooling

device is controlled so that the temperature of the refrigerant flowing through the heat

radiator side loop (the refrigerant circulation loop) indicated by the arrow A in Fig. 1 is

decreased, and then, the refrigerant is caused to flow through the heat receiver side loop

(the refrigerant circulation loop) indicated by the arrow B in Fig. 1 on condition that the

net positive suction head becomes the predetermined value or more.

[0018]

An example of a more specific control step of the control method related to the

minimum configuration is as follows.

SP1

The control unit 7 uses measurement data and known data for an inlet pressure of the pump 6, a detection value of the temperature, and a physical property value of the refrigerant (for example, a saturated vapor pressure at the temperature) as parameters, to detect the net positive suction head through calculation based on Equation (1) above.

SP2

The control unit 7 compares the net positive suction head with a management

value (a predetermined value) of the net positive suction head obtained in advance.

SP3

The control unit 7 starts the operation of the pump 6 on condition that the net

positive suction head exceeds the predetermined value.

[0019]

According to the above configuration, because the pump 6 is activated on

condition that a pressure of the refrigerant liquid to be sucked is equal to or higher than a

predetermined net positive suction head according to the saturated vapor pressure at that

point in time, it is possible to prevent cavitation on the suction side of the pump 6 from

occurring.

[0020]

(First Embodiment)

Hereinafter, a first embodiment of the present invention will be described with

reference to Figs. 3 and 4. In Fig. 4, the same components as those in Fig. 1 are denoted

by the same reference signs, and a description thereof will be simplified.

The heat receiver 1 is provided in, for example, a ceiling-mounted unit disposed

above a heat generation source such as an internal server of a server room or the like, and

includes, for example, a pipe through which a refrigerant flows, and fins having a contact

area necessary to promote heat exchange with an exhaust gas of a server that is a cooling

target. Further, the heat receiver 1 functions as an evaporator that receives heat from the air that absorbs heat of an internal heat generation source by passing through the inside of the server, is discharged to a hot aisle side of the server room (a passage in the server room on the side from which cooling air having a raised temperature is discharged), and has become an updraft to be brought into contact with the fins, and the refrigerant flowing inside evaporates according to an amount of received heat. The refrigerant that has received the heat in the heat receiver 1 becomes a gas phase refrigerant according to the amount of received heat, and is discharged in a gas-liquid mixed phase state.

A pipe 8a connects the heat receiver 1 to a gas-liquid separator (specifically, a

closed tank, which is hereinafter referred to as a tank) 5, and a pipe 8b connects the gas

phase portion (an upper portion) of the tank 5 to the suction side of the compressor 2.

[0021]

A pipe 8c connects a discharge side of the compressor 2 to the heat radiator 3.

The heat radiator 3 is installed, for example, outside in a building including the server

room, and radiates heat by heat-exchanging the refrigerant compressed by the

compressor 2 with, for example, an atmosphere, so that the refrigerant is below a boiling

point and becomes a liquid phase refrigerant.

A pipe 8d connects the heat radiator 3 to the expansion valve 4. Therefrigerant

that has radiated the heat in the heat radiator 3 and become a liquid phase refrigerant

expands in the expansion valve 4 as an expander.

A pipe 8e supplies the refrigerant that has expanded by the expansion valve 4

and entered a gas-liquid mixed phase state to the tank 5.

[0022]

A pipe 8f connects a portion below a liquid level L of the tank 5 to the suction

side of the pump 6, and a pipe 8g connects a discharge side of the pump 6 to the heat

receiver 1. A valve V that opens or closes a flow path of the refrigerant is provided in the middle of the pipe 8g. When a plurality of heat receivers 1 are provided in parallel in one refrigeration cycle (a system of the refrigerant flowing through a heat receiver side loop B), it is possible to distribute a required amount of refrigerant according to the difference in amount of received heat between the plurality of heat receivers 1 and the difference in flow path resistance of the pipe 8g directed to the respective heat receivers 1 by adjusting the degree of opening of each valve V provided in the pipe 8g directed to each heat receiver 1.

The liquid phase refrigerant obtained by the gas-liquid separation in the tank 5 is

sucked into the pump 6 via the pipe 8f and supplied to the heat receiver 1 via the pipe 8g.

Then, in the heat receiver 1, heat is received from a heat generation source such as an

exhaust gas of the server, the refrigerant flows into the tank 5 again and circulates in the

refrigeration cycle.

[0023]

A temperature sensor T measures the temperature of the refrigerant at a position

immediately before the refrigerant is sucked into the pump 6 in the middle of the pipe 8f,

and a pressure sensor P similarly measures the pressure of the refrigerant at the position

immediately before the refrigerant is sucked into the pump 6.

[0024]

The control unit 7 controls the activation of the pump 6 from data of the

temperature and the pressure supplied from the temperature sensor T and the pressure

sensor P, and a calculation equation for a required suction head stored in a database DB.

The database DB1 is mounted in a memory as a control program or stored data in the

control unit 7, or is stored in a server physically separated from the control unit 7 and

receives or sends data via a communication line. Details of control of the control unit 7

will be described below together with an operation of the cooling device with reference to Fig. 3.

[0025]

Control content of the control unit 7 will be described together with an operation

of the cooling device of the first embodiment having the configuration of Fig. 3 with

reference to a flowchart of Fig. 3.

SP11

Control is executed on condition that the compressor 2 is activated so that the

refrigerant circulates through the heat radiator side loop A. The heat radiator 3 is

activated, for example, by activating a fan (not illustrated) to supply cooling air (outside

air) or by activating a pump (not illustrated) to supply cooling water, and is activated by

opening the valve constituting the expander 4 to a predetermined degree of opening.

SP12

The control unit 7 controls a drive motor of the compressor 2 to gradually

increase the pressure of the refrigerant to a predetermined compression ratio.

SP13

The control unit 7 acquires the data of the temperature and the pressure of the

refrigerant on the inlet side of the pump 6 from the temperature sensor T and the pressure

sensor P.

SP14

The control unit 7 refers to the database DB to calculate a density of the

refrigerant liquid and the saturated vapor pressure from the temperature supplied from

the temperature sensor T. Further, the control unit 7 calculates the required suction head

according to

Net positive suction head = (pump inlet pressure - saturated vapor

pressure)/(density of refrigerant liquid x gravitational acceleration) --- (1) described above.

In the calculation of the net positive suction head based on Equation (1) above, a

pump inlet pressure P, a refrigerant temperature T decreases with the increase in pressure

of the refrigerant by the compressor 2, and the saturated vapor pressure decreases with a

decrease in the refrigerant temperature. In the first embodiment, it is assumed that the

density of the refrigerant is constant regardless of change in the refrigerant temperature T.

Further, a threshold value of the net positive suction head is calculated by using

Equation (2) below.

Threshold value =f x (net positive suction head - required suction head) ---

(2)

Here, the required suction head is the minimum suction pressure that does not

cause cavitation, which is determined by performance characteristics of the pump 6 (a

flow rate and pressure characteristics determined by design or obtained by actual

measurement), and the coefficient f is a safety factor that is multiplied to reliably prevent

cavitation in consideration of operating conditions or a measurement error.

[0026]

SP15

The control unit 7 determines whether the net positive suction head has

exceeded the threshold value, returns to SP13 and waits for the net positive suction head

to increase in the case of No, and proceeds to the next step in the case of Yes.

SP16

The control unit 7 activates the pump 6.

SP17

The control unit 7 activates the heat receiver 1. Specifically, the valve V is

opened so that the refrigerant sucked from the tank 5 is supplied to the heat receiver 1.

Further, a fan (not illustrated) provided in the heat receiver 1 is activated, air in the server

room is sucked and sent to the heat receiver 1, and the air exchanges the heat with the

refrigerant.

SP18

The refrigerant circulates in the refrigeration cycle through the above steps, and

the compressor 2 continuously compresses the refrigerant. That is, an operation of the

refrigeration cycle in which the refrigerant received in the heat receiver side loop B is

compressed and heat-radiated in the heat radiator side loop A and supplied to the heat

receiver side loop B again continues.

[0027]

In the first embodiment, because the net positive suction head of the pump 6 can

be maintained above the required suction head, it is possible to stably supply the

refrigerant from the pump 6 to the heat receiver 1 without causing cavitation immediately

after the start of the operation of the refrigeration cycle.

[0028]

(Second Embodiment)

A second embodiment of the present invention will be described with reference

to Fig. 5. In Fig. 5, the same components as those in Figs. 1 and 4 are denoted by the

same reference signs and description thereof will be simplified.

In the second embodiment, a suction side and a discharge side of a pump 6 are

connected by a pipe (a bypass pipeline) 8h, and a bypass valve 9a is provided in the

middle of the pipe 8h.

[0029]

Even in this second embodiment, the control unit 7 performs control in the same

processing steps SP11 to SP18 as the flowchart illustrated in Fig. 3 that is executed in the first embodiment.

In the second embodiment, because an amount of refrigerant according to a

degree of opening of the bypass valve 9a can be circulated from the discharge side to the

suction side of the pump 6 by the bypass pipeline 8h, it is possible to cause the pump 6 to

suck the refrigerant having a flow rate equal to or higher than a predetermined value,

which is difficult to cause the cavitation, and because the temperature rise of the

refrigerant that repeatedly passes through the pump 6 due to the circulation of the

refrigerant via the bypass pipeline 8h, that is, the temperature is measured by the

temperature sensor T between a confluence portion of the bypass pipeline 8h and the pipe

8f and the suction side of the pump 6, it is possible to accurately reflect this rise of

temperature in the saturated vapor pressure for each temperature in a calculation equation

for a net positive suction head and accurately calculate the net positive suction head even

when the temperature of the refrigerant rises with the circulation through the bypass

pipeline 8h.

[0030]

(Third Embodiment)

A third embodiment of the present invention will be described with reference to

Figs. 6 and 7. In Fig. 7, the same components as those in Figs. 1, 4, and 5 are denoted

by the same reference signs, and description thereof will be simplified.

In the fifth embodiment, the refrigerant temperature and refrigerant pressure in a

tank 5 are adopted instead of a refrigerant temperature and refrigerant pressure at an inlet

of a pump 6 of the first and second embodiments as parameters of the calculation

equation for a net positive suction head that are used for control of the pump 6 by a

control unit 7, and a liquid level height of the refrigerant in the tank 5 is used.

Specifically, the tank 5 includes a temperature sensor T that detects the refrigerant temperature at a bottom (a position at which a liquid phase state is guaranteed), and a pressure sensor P that detects the refrigerant pressure at an upper portion (a position at which a gas phase state is guaranteed). Further, the tank 5 includes, at an upper portion, a liquid level sensor L that detects a liquid level sensor L of the liquid phase refrigerant stored in the tank 5.

That is, the control unit 7 includes a database DB2 that receives measurement

data from the pressure sensor P, the refrigerant temperature sensor T, and the liquid level

sensor L to calculate the net positive suction head, and the database DB2 calculates the

net positive suction head on the basis of Equation (') below.

Net positive suction head = liquid level height in gas-liquid separator + (pressure

inside gas-liquid separator - pipe pressure loss - saturated vapor pressure)/(refrigerant

liquid density x gravitational acceleration) - - (1')

The pipe pressure loss can be calculated by multiplying a flow rate of the

refrigerant (determined by a flow velocity and a pipe diameter) by a predetermined

pressure loss coefficient K.

[0031]

of the cooling device of the third embodiment with reference to a flowchart of Fig. 6.

SP11

Control is started on condition that the refrigerant circulates through the heat

radiator side loop A due to the activation of the compressor 2.

SP12

The control unit 7 controls a drive motor of the compressor 2 to gradually

increase the pressure of the refrigerant to a predetermined compression ratio.

SP13"

The control unit 7 acquires the data of the temperature and the pressure of the

refrigerant in the tank 5 from the temperature sensor T and the pressure sensor P, and

acquires the data of the liquid level in the tank 5 from the liquid level sensor L.

SP14'

The control unit 7 refers to the database DB2 to calculate the density of the

the temperature sensor T. Further, the control unit 7 calculates a required suction head

according to

liquid density x gravitational acceleration) --- (1') described above.

In the calculation of the net positive suction head based on Equation (') above,

a refrigerant temperature T decreases with the increase in pressure of the refrigerant by

the compressor 2, and the saturated vapor pressure decreases with a decrease in the

refrigerant temperature. Further, from the liquid level height, a pressure applied to the

liquid level height in the tank 5 is reflected in the effective charging head. In the third

embodiment, it is assumed that the density of the refrigerant is constant regardless of

change in the refrigerant temperature T.

[0032]

SP15

The control unit 7 determines whether the net positive suction head has

exceeded the threshold value obtained by Equation (2) common to the first and second

embodiments, returns to SP13' and waits for the net positive suction head to rise in the

case of No, and proceeds to the next step in the case of Yes.

SP16

The control unit 7 activates the pump 6.

SP17

The control unit 7 activates the heat receiver 1. Specifically, the valve V is

refrigerant.

SP18

receiver side loop B again continues.

[0033]

According to the above configuration, it is possible to calculate the required

suction head that can prevent the occurrence of cavitation of the pump 6, by using the

data acquired by the sensors provided in order to measure the pressure, the temperature,

and the liquid level in the tank 5 without separately providing sensors in the pipe 8f of a

suction portion of the pump 6.

[0034]

(Fourth Embodiment)

A fourth embodiment of the present invention will be described with reference

to Figs. 8 and 9. In Fig. 9, the same components as those in Figs. 1, 4, and 7 are

denoted by the same reference signs, and a description thereof will be simplified.

In the fourth embodiment, a control unit 7 performs control according to a waiting time until the start of an operation of a pump 6 stored in a database DB3.

A waiting time is determined on the basis of, for example, the amount of

increase in pressure according to an operating time of the compressor 2 until the pressure

on the suction side of the pump 6 reaches the net positive suction head that does not

cause cavitation on the basis of operation record data of the refrigeration cycle for each

outside air temperature, and is calculated by Equation (3) below.

Waiting time = KT x amount of increase in pressure of compressor -- (3)

KT is a time sufficient for the refrigerant temperature to begin to decrease with

an increase in the pressure, and is an integer that is determined on the basis of operation

record data for a degree of increase in pressure of the refrigeration cycle and occurrence

or non-occurrence of the cavitation (an operation situation of the pump), and used for

converting the amount of increase in pressure required for the compressor until the

refrigerant temperature decreases into a waiting time.

[0035]

of the cooling device of the fourth embodiment with reference to the flowchart of Fig. 8.

SP1l

Control is executed on condition that the compressor 2 is operated and the

refrigerant is circulated in the refrigeration cycle.

SP12

The control unit 7 controls a drive motor of the compressor 2 to gradually

increase the pressure of the refrigerant to a predetermined compression ratio.

SP13"

The control unit 7 acquires data of the waiting time calculated on the basis of

Equation (3) above from the database DB3.

SP15'

The control unit 7 determines whether or not the waiting time exceeds a

threshold value preset in the database DB3, waits Yes (the waiting time exceeds the

threshold value), and proceeds to the next step.

SP16

The control unit 7 activates the pump 6.

SP17

The control unit 7 activates the heat receiver 1. Specifically, the valve V is

refrigerant.

SP18

receiver side loop B again continues.

[0036]

According to the above configuration, it is possible to prevent the occurrence of

cavitation by waiting for the operation of the pump 6 over a predetermined time when the

pressure of the refrigerant is expected to reach the net positive suction head of the pump

6. Further, the control may be selected from a plurality of waiting time threshold values

according to, for example, the outside air temperature according to seasonal factors, and

the room temperature of the server room according to a variation in a load of a server that is a cooling target. Further, because this control is executed on the basis of the passage of a preset time, it is not necessary to provide sensors at various places of the refrigeration cycle to measure pressure, temperature, and the like, and it is possible to simplify the configuration of the refrigeration device. That is, it is possible to indirectly determine whether or not a condition that the net positive suction head has reached a predetermined pressure or higher is satisfied, by using a measurement value of time.

[0037]

Specific configurations of the heat receiver, the compressor, the heat radiator,

the gas-liquid separator, the expander, the pump, and the control unit that constitute the

refrigeration cycle are not limited to the embodiments and, of course, may be changed

without departing from the gist of the present invention. For example, the expander can

have a function of depressurizing and expanding a refrigerant in a flow path of the liquid

phase refrigerant by applying a throttle to the flow path, and an orifice (simply, a throttle)

or a capillary (which is a thin tube having a predetermined length formed in a coil shape,

and gives resistance to a fluid by flowing through a flow path having a small

cross-sectional area) can be adopted, in addition to the valve in the embodiment.

[0038]

Further, activation control for the pump 6 that is performed in the first to fourth

embodiments is not limited to a single implementation, and a plurality of controls may be

implemented in combination. Further, when the plurality of controls may be

implemented in combination, any one of the controls may be preferentially executed in

consideration of conditions such as a response speed to an increase or decrease of the net

positive suction head, and an influence on loads of refrigeration cycles of other systems.

INDUSTRIAL APPLICABILITY

[0039]

The cooling device and cooling method of the present invention can be used for

air conditioning for a data center and the like.

Reference Symbols

[0040]

1 Heat receiver

2 Compressor

3 Heat radiator

3a Fan

3b Cooling air adjustment plate

4 Expander

5 Gas-liquid separator (tank)

6 Pump

7 Control unit

8a, 8b, 8c, 8d, 8e, 8f, 8g, 8h Pipe

9a Bypass valve

DB1, DB1', DB2, DB3 Database

T Temperature sensor

P Pressure sensor

L Liquid level sensor

V Valve

Claims

1. A cooling device using a refrigeration cycle in which a refrigerant is circulated

through a heat receiver, a compressor, a heat radiator, and an expansion valve, the

cooling device comprising:

a gas-liquid separator configured to perform gas-liquid separation on the

refrigerant supplied from the expansion valve;

a pump configured to send a liquid phase refrigerant separated by the gas-liquid

separator to the heat receiver; and

a control unit configured to control opening and closing of a refrigerant flow

path of the refrigeration cycle, and an operation and stop of the compressor and the

pump,

wherein the control unit starts the operation of the pump on condition that a net

positive suction head of the pump has reached a predetermined value or more.

2. The cooling device according to claim 1, wherein the control unit calculates the

net positive suction head using a pressure between the pump and the gas-liquid separator,

a saturated vapor pressure of the refrigerant, and a liquid density of the refrigerant.

3. The cooling device according to claim 1, wherein the control unit calculates the

net positive suction head from detection data of a pressure sensor and a temperature

sensor, the pressure sensor being configured to measure a pressure of a liquid phase

portion between the pump and the gas-liquid separator, the temperature sensor being

configured to measure a temperature of the refrigerant.

4. The cooling device according to claim 1, wherein the control unit calculates the

portion between the pump and the gas-liquid separator and inside a bypass valve pipe

configured to connect a front and a rear of the pump, the temperature sensor being

configured to measure a temperature of the refrigerant.

5. The cooling device according to claim 1, wherein the control unit calculates the

net positive suction head using a liquid level height inside the gas-liquid separator, a

pressure of a gas phase portion, a saturated vapor pressure of the refrigerant, and a

density of the refrigerant.

6. The cooling device according to claim 1, wherein the control unit calculates the

net positive suction head from detection data of a liquid level sensor, a pressure sensor

and a temperature sensor, the liquid level sensor being configured to measure a liquid

level of the gas-liquid separator, the pressure sensor being configured to measure a

pressure of a gas phase portion of the gas-liquid separator, the temperature sensor being

configured to measure a temperature of the refrigerant in the gas-liquid separator.

7. The cooling device according to claim 1, wherein the control unit starts an

operation of the pump on condition that a predetermined time has elapsed after activation

of the compressor.

8. A control method for a cooling device using a refrigeration cycle in which a

refrigerant is circulated through a heat receiver, a compressor, a heat radiator, and an expansion valve, the control method comprising: controlling, by a control unit, an operation of a pump configured to send, to the heat receiver, a liquid phase refrigerant separated by a gas-liquid separator configured to perform gas-liquid separation on the refrigerant supplied from the expansion valve; and starting, by the control unit, the operation of the pump on condition that a net positive suction head of the pump has reached a predetermined value or more.