Turbo freezing machine and start-up control method therefor

Abstract

The present invention is provided with: a turbo compressor that compresses a refrigerant; a condenser that condenses the refrigerant compressed by the turbo compressor; an expansion valve that expands a liquid refrigerant introduced from the condenser; an evaporator that evaporates the refrigerant expanded by the expansion valve; an oil tank that stores a lubricating oil supplied to the turbo compressor; a pressure equalizing pipe that connects the oil tank and the evaporator; and a control unit that controls start-up. The control unit calculates the amount of a refrigerant eluded into the lubricating oil in the oil tank at the time of start-up, and reduces a pressure reduction speed in the oil tank by limiting the opening operation of an IGV when the refrigerant elution amount per prescribed time exceeds a prescribed value.

Claims

1. A centrifugal chiller comprising: a turbo compressor which compresses a refrigerant; a condenser which condenses the refrigerant compressed by the turbo compressor; an expansion valve which expands a liquid refrigerant introduced from the condenser; an evaporator which evaporates the refrigerant expanded by the expansion valve; an oil tank which stores a lubricant to be supplied to the turbo compressor; a pressure equalizing pipe which connects the oil tank and the evaporator to each other; and a controller which controls start-up, wherein at the time of the start-up, the controller calculates an elution amount of the refrigerant eluted from the refrigerant dissolved into the lubricant in the oil tank, and decreases a pressure reduction speed in the oil tank in a case where the refrigerant elution amount per a predetermined time period exceeds a predetermined value, wherein the oil tank includes a temperature sensor and a pressure sensor, wherein refrigerant dissolution amount information indicating a relationship between a temperature and a pressure, and a refrigerant dissolution amount with respect to the lubricant is stored in the controller, wherein the controller calculates the refrigerant elution amount, based on an oil tank temperature obtained from the temperature sensor, an oil tank pressure obtained from the pressure sensor, and the refrigerant dissolution amount information, and wherein a change in the refrigerant elution amount increases as the pressure decreases, and in a case where comparison is performed at the same pressure, the change decreases as the temperature increases.

2. The centrifugal chiller according to claim 1, wherein the turbo compressor includes suction refrigerant control means for controlling a flow rate of the refrigerant sucked by the turbo compressor, and wherein the controller decreases the pressure reduction speed in the oil tank by decreasing the flow rate of the sucked refrigerant by the suction refrigerant control means.

3. The centrifugal chiller according to claim 1, wherein in a case where the refrigerant elution amount per the predetermined time is equal to or less than the predetermined value, the controller increases the pressure reduction speed in the oil tank.

4. A start-up method for a centrifugal chiller including a turbo compressor which compresses a refrigerant, a condenser which condenses the refrigerant compressed by the turbo compressor, an expansion valve which expands a liquid refrigerant introduced from the condenser, an evaporator which evaporates the refrigerant expanded by the expansion valve, an oil tank which stores a lubricant to be supplied to the turbo compressor, a pressure equalizing pipe which connects the oil tank and the evaporator to each other, and a controller which controls start-up, the method comprising: at the time of the start-up, calculating an elution amount of the refrigerant eluted from the refrigerant dissolved into the lubricant in the oil tank, and decreasing a pressure reduction speed in the oil tank in a case where the refrigerant elution amount per a predetermined time period exceeds a predetermined value, wherein the oil tank includes a temperature sensor and a pressure sensor, wherein refrigerant dissolution amount information indicating a relationship between a temperature and a pressure, and a refrigerant dissolution amount with respect to the lubricant is stored in the controller, wherein the controller calculates the refrigerant elution amount, based on an oil tank temperature obtained from the temperature sensor, an oil tank pressure obtained from the pressure sensor, and the refrigerant dissolution amount information, and wherein a change in the refrigerant elution amount increases as the pressure decreases, and in a case where comparison is performed at the same pressure, the change decreases as the temperature increases.

Description

BRIEF DESCRIPTION OF DRAWINGS

(1) FIG. 1 is a schematic configuration diagram showing a centrifugal chiller according to an embodiment of the present invention.

(2) FIG. 2 is a graph showing a relationship between a pressure and a temperature, and a refrigerant dissolution amount.

(3) FIG. 3 is a graph showing a temporal change of a refrigerant elution amount at the time of start-up of the centrifugal chiller.

DESCRIPTION OF EMBODIMENTS

(4) Hereinafter, an embodiment according to the present invention will be described with reference to the drawings.

(5) As shown in FIG. 1, a centrifugal chiller 1 includes a turbo compressor 3 which compresses a refrigerant, a condenser 5 which condenses a high-temperature and high-pressure gas refrigerant compressed by the turbo compressor 3, an expansion valve 7 which expands a liquid refrigerant introduced from the condenser 5, and an evaporator 9 which evaporates the liquid refrigerant expanded by the expansion valve 7.

(6) As the refrigerant, a low pressure refrigerant referred to as HFO-1233zd (E) is used.

(7) The turbo compressor 3 is a centrifugal compressor and is driven by an electric motor 11 whose rotating speed is controlled by an inverter. An output of the inverter is controlled by a controller (not shown). An inlet guide vane (suction refrigerant control means: hereinafter, referred to as IGV) 13 which controls a flow rate of a sucked refrigerant is provided in a refrigerant suction port of the turbo compressor 3, and thus, capacity of the centrifugal chiller 1 can be controlled by the IGV 13. An opening degree control of the IGV 13 is performed by the controller.

(8) The turbo compressor 3 includes an impeller 3a which rotates around a rotary shaft 3b. Rotational power is transmitted from the electric motor 11 to the rotary shaft 3b via a speed increasing gear 15. The rotary shaft 3b is supported by a bearing 3c.

(9) The condenser 5 is a shell and tube type heat exchanger or a plate type heat exchanger.

(10) Cooling water for cooling the refrigerant is supplied to the condenser 5. Heat of the cooling water introduced to the condenser 5 is discharged to the outside by a cooling tower (not shown) or an air heat exchanger (not shown), and thereafter, the cooling water is introduced to the condenser 5 again.

(11) The expansion valve 7 is an electric expansion valve, and an opening degree of the expansion valve 7 is set to a predetermined value by the controller.

(12) The evaporator 9 is a shell and tube type evaporator or a plate type evaporator. Chilled water supplied to an external load (not shown) is introduced to the evaporator 9. The chilled water is cooled to a rated temperature (for example, 7 C.) by heat exchange between the chilled water and the refrigerant in the evaporator 9, and is fed to the external load.

(13) The lubricant is supplied from the oil tank 17 to the bearing 3c of the turbo compressor 3 or the speed increasing gear 15. For example, as the lubricant, a mineral oil having a viscosity grade of 100 is used.

(14) An oil pump (not shown) is provided in the oil tank 17, and thus, the lubricant is supplied through an oil supply pipe 19 at a predetermined flow rate. The lubricant which has lubricated the inside of the turbo compressor 3 is returned to the oil tank 17 via an oil return pipe 21.

(15) A pressure equalizing pipe 23 which communicates with a portion between the oil tank 17 and the evaporator 9 is provided between the oil tank 17 and the evaporator 9, and a pressure in the oil tank 17 and a pressure in the evaporator 9 are equalized to each other. In this way, the pressure in the oil tank 17 decreases, and thus, a refrigerant dissolution amount with respect to the lubricant is kept low.

(16) A pressure sensor 25 and a temperature sensor 27 are provided in the oil tank 17. The pressure in the oil tank 17 is measured by the pressure sensor 25, and a measurement result is output to the controller. The temperature (specifically, the temperature of the lubricant) in the oil tank 17 is measured by the temperature sensor 27, and a measurement result is output to the controller.

(17) The controller controls an operation of the centrifugal chiller 1 such as a start-up control or the like of the centrifugal chiller 1 and includes, for example, a Central Processing Unit (CPU), a Random Access Memory (RAM), a Read Only Memory (ROM), a computer readable storage medium, or the like. For example, a series of processing for realizing various functions is stored in a storage medium or the like in the form of a program. The CPU causes a RAM or the like to read the program and executes information processing/calculation processing to realize various functions. The program may be installed in the ROM or other storage mediums in advance, may be provided in a state of being stored in a computer readable storage medium, or may be delivered via wired or wireless communication means. The computer-readable storage medium is a magnetic disk, a magneto-optical disk, a CD-ROM, a DVD-ROM, a semiconductor memory, or the like.

(18) In the controller, as shown in FIG. 2, refrigerant dissolution amount information relating to the refrigerant dissolution amount is stored in a storage area. In addition, a description format of this refrigerant dissolution amount information may be a map format or a relational expression using an approximate expression or the like.

(19) In FIG. 2, a horizontal axis indicates the refrigerant dissolution amount indicating the dissolution amount of the refrigerant with respect to the lubricant, and a vertical axis indicates a pressure. Each curve shown in FIG. 2 indicates the refrigerant dissolution amount at each temperature. As can be seen from FIG. 2, each curve has a convex shape, the refrigerant dissolution amount decreases as the pressure decreases, and a change in the refrigerant dissolution amount decreases as the pressure decreases. In addition, in a case where comparison is performed at the same pressure, it is understood that the refrigerant dissolution amount decreases as the temperature increases.

(20) As shown in FIG. 2, the controller calculates the refrigerant elution amount at each time using the refrigerant dissolution amount information. Here, the refrigerant elution amount means an amount [% by weight] of the refrigerant which is dissolved into the lubricant to be gasified and is discharged from the lubricant.

(21) As shown in FIG. 2, in a case where the temperature in the oil tank 17 measured by the temperature sensor 27 is 40 C., a refrigerant dissolution amount D1 is obtained from a pressure P1 before 10 seconds measured by the pressure sensor 25, a refrigerant dissolution amount D2 is obtained from a decreased pressure P2 after 10 seconds measured by the pressure sensor 25, and thereafter, the refrigerant elution amount is calculated from a difference (D1D2) therebetween. In this way, in the controller, the calculation of the refrigerant elution amount is performed at predetermined time intervals (10 seconds interval in the example of FIG. 2).

(22) Next, the start-up control of the centrifugal chiller 1 having the above-described configuration will be described.

(23) Before the start-up of the centrifugal chiller 1, temperatures of the condenser 5 and the evaporator 9 are near an ambient temperature, and the pressure in the condenser 5 and the pressure in the evaporator 9 are approximately the same as each other. In this state, if the centrifugal chiller 1 starts-up, the turbo compressor 3 is rotated by a command of the controller, and the refrigerant sucked via the IGV 13 is discharged from the turbo compressor 3. The refrigerant discharged from the turbo compressor 3 is fed to the condenser 5, and circulates to be returned to the turbo compressor 3 again through the expansion valve 7 and the evaporator 9. A speed of the turbo compressor 3 is gradually increased by the command of the controller, and accordingly, the IGV 13 is controlled be opened gradually from a fully closed state.

(24) In this way, if the centrifugal chiller 1 starts-up, the pressure in the evaporator 9 gradually decreases. Accordingly, the pressure in the oil tank 17 connected to the evaporator 9 by the pressure equalizing pipe 23 is gradually decreased. The pressure in the oil tank 17 is measured by the pressure sensor 25 to be sent to the controller, and the temperature in the oil tank 17 is measured by the temperature sensor 27 to be sent to the controller.

(25) In the controller, as described with reference to FIG. 2, the refrigerant elution amount is calculated for each predetermined time (for example, 10 seconds) from the obtained pressure and temperature of the oil tank 17. FIG. 3 shows an example in which the refrigerant elution amount is calculated at each time and is plotted. As shown in FIG. 3, at the beginning of the start-up, the pressure reduction speed is large. Accordingly, the refrigerant elution amount tends to increase, and thereafter, the pressure reduction speed decreases, and the refrigerant elution amount tends to decrease.

(26) In a case where the refrigerant elution amount per the predetermined time exceeds a predetermined value, for example, in a case where the refrigerant elution amount exceeds the predetermined value during 30 seconds, as shown by a vane opening regulation start in FIG. 3, the controller performs the control to stop an opening operation of the IGV 13. In addition, instead of stopping the opening operation of the IGV 13, a speed of the opening operation of the IGV 13 may decrease. Accordingly, the pressure reduction speed in the oil tank 17 decreases or becomes 0, and foaming in the oil tank 17 is prevented in advance.

(27) A start timing of the control for regulating the opening degree of the IGV 13 is determined by obtaining a condition under which foaming occurs in the oil tank 17 by a preliminary test or the like and obtaining the refrigerant elution amount per a predetermined time period which does not reach this condition.

(28) In a case where after the opening degree of the IGV 13 is regulated, the refrigerant elution amount decreases, and the refrigerant elution amount per a predetermined time period is equal to or less than the predetermined value, for example, in a case where the refrigerant elution amount is equal to or less than the predetermined value during 30 seconds, as shown by a vane opening regulation release in FIG. 3, the controller performs the control such that the opening operation of the IGV 13 is performed again at a normal speed. Accordingly, it is returned to a normal start-up sequence, and thus, the opening operation of the IGV 13 proceeds, and the start-up operation of the centrifugal chiller 1 is performed.

(29) As described above, according to the present embodiment, the following effects are exerted.

(30) At the time of the start-up of the centrifugal chiller 1, in a case where the refrigerant elution amount per a predetermined time period exceeds the predetermined value, it is determined that there is a concern that the foaming occurs, the opening operation of the IGV 13 is regulated to decrease the pressure reduction speed in the oil tank 17. Accordingly, the foaming in the oil tank 17 is suppressed, lowering of an oil level in the oil tank 17 is prevented, and thus, it is possible to avoid a lubrication failure of the turbo compressor 3. In addition, the oil level in the oil tank 17 is not lowered, it is not necessary to add the lubricant so as to recover a predetermined oil level, and it is possible to suppress an increase in a cost.

(31) The refrigerant dissolution amount with respect to the lubricant depends on the pressure and the temperature. In addition, the refrigerant dissolution amount information between the pressure and the temperature, and the refrigerant dissolution amount is stored in the controller, and the refrigerant elution amount is calculated based on the measurement results from the pressure sensor 25 and the temperature sensor 27 of the oil tank 17. Accordingly, it is possible to obtain the refrigerant elution amount for each predetermined time, and it is possible to reliably suppress the occurrence of the foaming.

(32) In a case where the refrigerant elution amount per a predetermined time period is equal to or less than the predetermined value, it is determined that a possibility of occurrence in the foaming is low, and the pressure reduction speed in the oil tank 17 increases. Accordingly, it is possible to speed up the start-up of the centrifugal chiller 1 by returning the start-up to the normal start-up sequence.

(33) Moreover, in the above-described embodiment, the opening operation of the IGV 13 is regulated to decrease the pressure reduction speed in the oil tank 17. However, instead of this, in addition to the opening operation regulation of the IGV 13, the rotating speed of the turbo compressor 3 may decrease or the opening degree of the expansion valve 7 may be controlled in the opening direction so as to decrease the pressure reduction speed.

(34) In addition, HFO-1233zd (E) is described as an example of the low pressure refrigerant. However, the present invention can be applied to other low pressure refrigerants, or in a case where there is a concern that the foaming occurs in the oil tank, the present invention can be applied to a high pressure refrigerant.

REFERENCE SIGNS LIST

(35) 1: centrifugal chiller 3: turbo compressor 3a: impeller 3b: rotary shaft 3c: bearing 5: condenser 7: expansion valve 9: evaporator 11: electric motor 13: IGV (inlet guide vane: suction refrigerant control means) 15: speed increasing gear 17: oil tank 19: oil supply pipe 21: oil return pipe 23: pressure equalizing pipe 25: pressure sensor 27: temperature sensor