Ejector type cooling device

Abstract

To provide an ejector-type cooling device capable of further lowering a temperature of output hot water.SOLUTION: An ejector-type cooling device 10A includes: a condenser 18 for condensing a refrigerant; a refrigerant pump 12 for circulating the condensed refrigerant; a steam generator 14 to which the refrigerant is supplied to exchange heat with hot water to generate steam; an evaporator 20 connected so that the hot water flows in series at a downstream side with respect to the steam generator 14, and the refrigerant is supplied from a branch portion B1 between the condenser 18 and the refrigerant pump 12 through an expansion valve 22 to exchange heat with the hot water to be evaporated; an ejector 16 connected so that the refrigerant evaporated in the steam generator 14 is supplied to a drive flow port 16a and supplied to the condenser 18 from a discharge port 16b, and further the refrigerant supplied from the evaporator 20 is sucked from a suction port 16c; and an auxiliary heat exchanger 24 for cooling the hot water between the steam generator 14 and the evaporator 20 connected in series.SELECTED DRAWING: Figure 2

Description

[Technical field]

[0001] The present invention relates to an ejector-type cooling device. [Background technology]

[0002] For example, some circuits for circulating a refrigerant include an ejector. The ejector is configured to include a nozzle portion from which a driving fluid is ejected from an ejection port at the tip, a main body portion arranged to surround the periphery of the nozzle portion and having a hollow portion provided at a position on an extension of the ejection port of the nozzle portion, and a suction path connected to open into the hollow portion of the main body portion. In this ejector, when the refrigerant is ejected as a driving fluid from the ejection port of the nozzle portion, the external refrigerant is sucked into the hollow portion of the main body portion through the suction path, and the sucked suction fluid and the driving fluid are mixed, and then the pressure is increased in a diffuser and the mixture is discharged from a discharge port (see, for example, Patent Document 1). [Prior art documents] [Patent documents]

[0003] [Patent Document 1] JP 2008-64021 A Summary of the Invention [Problem to be solved by the invention]

[0004] In production equipment such as aluminum die casting machines, it is necessary to cool the molds. The hot water discharged from the equipment after cooling is cooled by an external cooling device, and the cooled hot water is then supplied to the production equipment again to be used as cooling water, forming a circulation system.

[0005] For example, the cooling device temporarily stores hot water from the production equipment in a water tank and releases heat to the air, then cools the hot water after heat release to a specified temperature using a chiller or the like, and supplies the cooled hot water to the production equipment again. In this case, the water tank is necessary because the hot water discharged from the production equipment is often hot, for example, at 70°C or higher, which is beyond the cooling capacity of the chiller. In this cooling device using a water tank, there is a problem that unused heat cannot be recovered due to the heat release of the hot water in the water tank, and the power consumption of the chiller increases.

[0006] For this reason, an ejector-type cooling device 500 as shown in Fig. 7 has been considered. The ejector-type cooling device 500 includes a refrigerant pump 502 that pressurizes and circulates the refrigerant, a steam generator 504 that performs heat exchange to recover thermal energy of high-temperature hot water W1 input from a flow path L1 to the refrigerant side, and an ejector 506 into which the refrigerant that has been pressurized by the refrigerant pump 502 and has had its thermal energy recovered by the steam generator 504 is introduced. The action of the ejector 506 is as described above.

[0007] The ejector-type cooling device 500 also includes an evaporator 508 that generates cold heat by the suction action of the ejector 506 and further cools the hot water W3 flowing out from the steam generator 504, and a condenser 510 that dissipates heat by heat exchange from the refrigerant flowing out from the ejector 506. A part of the refrigerant discharged from the condenser 510 is expanded and decompressed by an expansion valve 512 and supplied to the evaporator 508. In the ejector-type cooling device 500, the hot water flow paths of the steam generator 504 and the evaporator 508 are connected in series, and the hot water W1 is output as hot water W2 cooled in two stages using the steam generator 504 and the evaporator 508.

[0008] Such an ejector-type cooling device 500 does not require a water tank as described above, and can cool high-temperature hot water discharged from production equipment, etc., with a simple configuration and low power consumption, and return it to the production equipment, etc.

[0009] However, with the ejector-type cooling device 500, there is a concern that when the temperature of the hot water W1 supplied is relatively high due to the specifications of the production equipment connected to it or seasonal factors, the output hot water W2 may not be able to be lowered to the desired specified temperature.

[0010] The present invention has been made in consideration of the above problems, and an object of the present invention is to provide an ejector-type cooling device that can further reduce the temperature of the output hot water. [Means for solving the problem]

[0011] In order to solve the above-mentioned problems and achieve the object, the ejector type cooling device of the present invention is characterized by comprising: a condenser that condenses a gas phase refrigerant by heat exchange with cooling water; a refrigerant pump that pressurizes the refrigerant condensed in the condenser and circulates it; a steam generator to which the refrigerant discharged from the refrigerant pump is supplied and which evaporates the refrigerant by heat exchange with hot water; an evaporator to which hot water is connected so as to flow in series downstream of the steam generator, and to which the refrigerant is supplied from a branching part between the condenser and the refrigerant pump via an expansion valve and which evaporates the refrigerant by heat exchange with the hot water; an ejector connected to receive the refrigerant evaporated in the steam generator through a driving flow port and supply it to the condenser from a discharge port, and to suck the refrigerant supplied from the evaporator from a suction port; and an auxiliary cooler that cools the hot water between the steam generator and the evaporator connected in series.

[0012] This ejector-type cooling device is equipped with an auxiliary heat exchanger that cools hot water between the steam generator and evaporator connected in series, thereby improving cooling capacity and further reducing the temperature of the output hot water.

[0013] The cooling adjustment unit may be configured to adjust the capacity of the auxiliary cooler to cool the hot water, a first temperature detector to detect the temperature of the hot water flowing out from the evaporator, and a control unit to control the cooling adjustment unit so that the temperature detected by the first temperature detector is within a predetermined temperature range.

[0014] The auxiliary cooler may include an auxiliary heat exchanger that is supplied with a portion of the cooling water and exchanges heat with the hot water, and the cooling adjustment unit may be a flow rate adjustment valve that adjusts the flow rate of the cooling water supplied to the auxiliary heat exchanger. In this case, the auxiliary heat exchanger is supplied with a portion of the cooling water used in the condenser, so there is no need to prepare a separate dedicated cooling source.

[0015] The sub-cooler may include a forced air-cooled radiator, and the cooling adjustment unit may be a fan that blows air to the forced air-cooled radiator. When a forced air-cooled radiator is used, cooling water for the sub-cooler is not required.

[0016] The control unit may further control at least one of the expansion valve and the refrigerant pump so that the temperature detected by the first temperature detector is within a predetermined temperature range. By controlling the adjustment valve and the refrigerant pump, more accurate temperature control is possible.

[0017] The control unit may include a second temperature detector that detects the temperature of the refrigerant flowing into the evaporator, and the control unit may control the cooling adjustment unit based on a temperature difference between the temperature detected by the first temperature detector and the temperature detected by the second temperature detector. The first temperature detector and the second temperature detector detect the state of the evaporator, enabling control that utilizes the capacity of the evaporator. Effect of the Invention

[0018] The ejector-type cooling device of the present invention is provided with an auxiliary cooler that cools hot water between the steam generator and evaporator connected in series, thereby improving the cooling capacity and enabling the temperature of the output hot water to be further reduced. [Brief description of the drawings]

[0019] [Figure 1] FIG. 1 is a block diagram showing the configuration of a production system to which an ejector-type cooling device according to an embodiment of the present invention is applied. [Diagram 2] FIG. 2 is a circuit diagram showing the configuration of the ejector cooling device according to the first embodiment. [Figure 3A]FIG. 3A is a flowchart (part 1) showing a temperature control procedure of a control unit in the ejector-type cooling device according to the first embodiment. [Figure 3B] FIG. 3B is a flowchart (part 2) showing the temperature control procedure of the control unit in the ejector-type cooling device according to the first embodiment. [Figure 4] FIG. 4 is a diagram showing the temperature control range. [Diagram 5] FIG. 5 is a circuit diagram showing a configuration of an ejector cooling device according to the second embodiment. [Figure 6] FIG. 6 is a circuit diagram showing a configuration of an ejector cooling device according to the third embodiment. [Figure 7] FIG. 7 is a circuit diagram showing an ejector-type cooling device according to a comparative example. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0020] DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An ejector-type cooling device according to an embodiment of the present invention will be described in detail below with reference to the drawings. However, the present invention is not limited to the embodiment.

[0021] FIG. 1 is a block diagram showing the configuration of a production system to which an ejector-type cooling device 10 according to an embodiment of the present invention is applied. In this production system, an ejector-type cooling device 10 using an ejector is connected to a production device 11 such as an aluminum die-casting machine. The ejector-type cooling device 10 cools hot water W1 discharged from the production device 11 and heated to a high temperature of, for example, about 70° C., to hot water W2 of, for example, about 25° C., and returns the hot water W2 to the production device 11, which uses the cooled hot water W2 for cooling during production. That is, in this production system, a hot water circulation system is formed in which the ejector-type cooling device 10 cools the hot water used in the cooling process by the production device 11 after cooling and returns it to the production device 11 as hot water for cooling.

[0022] The object to be connected to the ejector-type cooling device 10 is not limited to the production device 11. A supply source that supplies hot water W1 to the ejector-type cooling device 10 and a supply destination that supplies hot water W2 to the ejector-type cooling device 10 may be different. Specific examples of the ejector-type cooling device 10 include an ejector-type cooling device 10A according to a first embodiment (see FIG. 2), an ejector-type cooling device 10B according to a second embodiment (see FIG. 5), and an ejector-type cooling device 10C according to a third embodiment (see FIG. 6).

[0023] 2 is a circuit diagram showing the configuration of an ejector-type cooling device 10A according to the first embodiment. The ejector-type cooling device 10A includes a refrigerant pump 12, a steam generator 14, an ejector 16, a condenser 18, an evaporator 20, and an expansion valve 22. The refrigerant pump 12 pressurizes the liquid-phase refrigerant and circulates it within a circuit. The steam generator 14 is supplied with the refrigerant discharged from the refrigerant pump 12 and evaporates the refrigerant by exchanging heat with hot water W1.

[0024] The ejector 16 supplies the refrigerant evaporated in the steam generator 14 to the driving flow port 16a and supplies it to the condenser 18. The condenser 18 condenses the gas-phase refrigerant supplied from the ejector 16 by heat exchange with cooling water. This cooling water is supplied through a branch B2 of a flow path L3 in the cooling water circuit. The cooling water supplied from the flow path L3 is mainly industrial water or a circulating cooling tower. The cooling water that has exchanged heat with the refrigerant in the condenser 18 is discharged from a flow path L4. The refrigerant condensed in the condenser 18 is introduced into the refrigerant pump 12 through a branch B1 of the refrigerant circuit and circulates through the circuit. A reservoir tank may be provided in the flow path flowing from the condenser 18 to the refrigerant pump 12.

[0025] The expansion valve 22 is provided between the branch point B1 of the refrigerant circuit and the evaporator 20, and controls the liquid phase refrigerant supplied from the condenser 18 so as to be at a predetermined low pressure.

[0026] The evaporator 20 evaporates the refrigerant supplied via the branch B1 and the expansion valve 22 by heat exchange with the hot water. The evaporator 20 is connected to the steam generator 14 so that the hot water flows in series downstream. The hot water W2 cooled by heat exchange with the refrigerant in the evaporator 20 is output from the flow path L2. In the evaporator 20, the refrigerant becomes a low-pressure refrigerant generated by the suction action of the ejector 16, and the latent heat is used to cool the hot water.

[0027] The refrigerant evaporated in the evaporator 20 is connected to be sucked from the suction port 16c of the ejector 16. In the ejector 16, the high-pressure refrigerant introduced from the driving flow port 16a is depressurized by the nozzle 16d and ejected. At this time, the refrigerant is sucked into the inside of the main body as a suction flow through the suction port 16c, and the driving flow and the suction flow are mixed and pressurized through the confluence / mixing section and the diffuser, and are ejected from the discharge port 16b. The nozzle depressurizes and accelerates the refrigerant, and the diffuser decelerates and pressurizes it. The nozzle may be a variable nozzle type so that the flow rate of the driving flow can be adjusted.

[0028] The ejector-type cooling device 10A further includes an auxiliary heat exchanger (auxiliary cooler) 24 and a flow rate adjustment valve (cooling adjustment unit) 26. The auxiliary heat exchanger 24 cools the hot water by exchanging heat with the cooling water, and is provided in series between the steam generator 14 and the evaporator 20. That is, of the hot water W3 between the steam generator 14 and the evaporator 20, the relatively high temperature W31 on the upstream side is cooled to the relatively low temperature W32 on the downstream side.

[0029] The cooling water that exchanges heat with the hot water in the auxiliary heat exchanger 24 branches at branch point B2 and is further supplied via a flow rate control valve 26. The cooling water that has exchanged heat with the hot water in the auxiliary heat exchanger 24 merges with the cooling water discharged from the condenser 18 at junction J and is discharged outside the system. The flow rate control valve 26 adjusts the amount of cooling water circulating, thereby adjusting the ability of the auxiliary heat exchanger 24 to cool the hot water. The cooling water used by the auxiliary heat exchanger 24 is supplied by branching off from branch point B2, so there is no need to prepare a separate dedicated cooling source.

[0030] As can be seen from Fig. 2, the hot water W1 is cooled in the order of the steam generator 14, the auxiliary heat exchanger 24, and the evaporator 20. The steam generator 14 is located at the most upstream position because a sufficient amount of heat is required for the input high-pressure refrigerant in order to output the refrigerant to the ejector 16 as a driving flow of high-temperature, high-pressure gas. The evaporator 20 is located at the most downstream position because, in order to effectively utilize the heat exchange capacity and sufficiently cool and output the hot water, it is necessary to exchange heat with the refrigerant whose temperature has been reduced by the expansion valve 22. Therefore, it is preferable to provide the auxiliary heat exchanger 24 for further cooling the hot water in series between the steam generator 14 and the evaporator 20.

[0031] In the ejector-type cooling device 10A, in order to further lower the temperature of the hot water W2 to be output, it is possible to increase the rotation speed of the refrigerant pump 12 to increase the amount of refrigerant supplied to the steam generator 14. However, since the steam generator 14 has the function of supplying a driving flow to the ejector 16 in addition to the function of cooling the supplied hot water W1, there is a limit to the amount of refrigerant that can be sufficiently gasified as the driving flow. Therefore, even if the condenser 18 has a margin in the capacity to dissipate heat from the refrigerant, the amount of refrigerant supplied to the steam generator 14 cannot be increased beyond a predetermined amount, and it is therefore desirable to provide an auxiliary heat exchanger 24 as another cooling means.

[0032] The ejector-type cooling device 10A is provided with a first temperature detector 30 that detects a temperature Ta of the hot water W2 output from the evaporator 20, and a second temperature detector 32 that detects a temperature Tb of the refrigerant supplied to the evaporator 20.

[0033] The ejector type cooling device 10A is equipped with a control unit (not shown). The control unit can read the temperature Ta from the first temperature detector 30 and the temperature Tb from the second temperature detector 32. The control unit adjusts the valve opening of the flow rate control valve 26, and can also adjust the rotation speed of the refrigerant pump 12 and the opening of the expansion valve 22. The control unit basically controls the flow rate control valve 26 and the like so that the temperature of the hot water W2 is within a predetermined temperature range.

[0034] The control unit is not limited by aspects such as the installation location, processing capacity, number of main processing units, and peripheral devices. The control unit may be realized, for example, by causing a processing device such as a CPU (Central Processing Unit) to execute a program, that is, by software, or by hardware such as an IC (Integrated Circuit), or by a combination of software and hardware.

[0035] Figure 3A is a flowchart (Part 1) showing the temperature control procedure of the control unit in the ejector type cooling device 10A, and Figure 3B is a flowchart (Part 2). Figure 4 is a diagram showing the temperature control range.

[0036] As shown in Figures 3A and 3B, the temperature control procedure is performed to maintain the temperature Ta within the range between T1u and T1d, that is, within the range of ΔT1 as shown in Figure 4. Furthermore, as a pre - processing step for this, it is controlled to be within the range between T2u and T2d, that is, within the range of ΔT2. However, T2u > T1u and T2d < T1d. The range of ΔT1 is the required appropriate temperature range for the hot water W2 to be output.

[0037] As shown in Figure 3A, first, in step S1, the control unit checks whether the detected temperature Ta is within the range of a predetermined low - temperature range ΔT1. When the detected temperature Ta is outside the range of ΔT1 (No), it moves to step S2. When the detected temperature Ta is within the range of ΔT1 (Yes), since no special adjustment is required, the current processing shown in Figure 3A ends.

[0038] Then, in step S2, if the temperature Ta is higher than T1u, it moves to step S3. If the temperature Ta is lower than T1d (α), it moves to step S11 in Figure 3B.

[0039] In step S3, the opening of the flow rate control valve 26 is increased by a predetermined small amount. However, the opening of the flow rate control valve 26 is adjusted within a range between a predetermined upper limit value and a predetermined lower limit value. By increasing the opening of the flow rate control valve 26, the cooling water flow rate of the auxiliary heat exchanger 24 increases, and the cooling effect is enhanced. In this way, it is expected that the temperature Ta will decrease. It is assumed that the refrigerant pump 12 is maintained at a predetermined rated rotation speed during the processing of steps S3 to S10.

[0040] In step S4, if the temperature Ta is higher than T2u (Yes), step S3 is repeatedly executed, and if it is lower (No), the process proceeds to step S5.

[0041] In step S5, if the temperature Ta is equal to or less than T2u and greater than T1u, the process proceeds to step S6. Otherwise, the temperature Ta is substantially within the range of ΔT1, and the current process in FIG. 3A is terminated.

[0042] In step S6, the temperature difference (Ta-Tb) between the temperature Ta of the hot water output from the evaporator 20 and the temperature Tb of the refrigerant supplied to the evaporator 20 is compared with a predetermined threshold value ΔTx. If Ta-Tb is equal to or greater than ΔTx (Yes), the process proceeds to step S7. If Ta-Tb is less than ΔTx (No), the process proceeds to step S9.

[0043] In step S7, the opening of the expansion valve 22 is increased by a predetermined small amount. Then, in step S8, step S7 is repeatedly executed until the temperature Ta falls within the range of ΔT1 (No), and if the temperature Ta falls within the range of ΔT1 (Yes), the current process in FIG. 3A is terminated.

[0044] In step S9, the opening of the expansion valve 22 is reduced by a predetermined small amount. Then, in step S10, step S9 is repeatedly executed until the temperature Ta falls within the range of ΔT1 (No), and if the temperature Ta falls within the range of ΔT1 (Yes), the current process in Fig. 3A is terminated. The processes of steps S7 to S10 are regarded as fine adjustments to the processes of steps S3 and S4.

[0045] In this way, the adjustment of temperature Ta in the ejector-type cooling device 10A incorporates control based on the temperature difference (Ta-Tb) between temperatures Ta and Tb. This is because, when the temperature difference (Ta-Tb) becomes small, the amount of heat exchange in the evaporator 20 decreases, the refrigerant does not become a gas but becomes a two-phase gas-liquid, and the efficiency of the ejector 16 decreases, resulting in a decrease in cooling performance. By keeping the temperature difference (Ta-Tb) at or above the threshold value ΔTx, the so-called pinch temperature is kept at an appropriate level, and the heat exchange capacity of the evaporator 20 is effectively utilized.

[0046] Furthermore, in order to perform temperature control based on the detailed state of the heat exchange performed by the evaporator 20, it is necessary to detect the drop in the hot water temperature and the rise in the refrigerant temperature in the evaporator 20. However, this requires detecting the inflow hot water temperature and outflow refrigerant temperature to the evaporator 20, which increases the number of detectors, leading to increased costs and complicated control. In contrast, in this embodiment, the heat exchange performed by the evaporator 20 is maintained in an optimal state by using two temperature detectors 30, 32, thereby reducing costs and simplifying control.

[0047] 3B basically performs the reverse process of steps S3 to S10 when the temperature Ta is lower than the range of ΔT1. That is, in step S11, the opening degree of the flow rate control valve 26 is reduced by a predetermined minute amount, which is the reverse of step S3. Then, steps S15 to S21 perform the reverse process of steps S4 to S10.

[0048] 3B, steps S12 to S14 are added in addition to the reverse processing of steps S3 to S10. In step S12 after step S11, it is confirmed whether the flow rate adjustment valve 26 is fully closed. If it is fully closed (Yes), the process proceeds to step S13, and if it is not fully closed (No), the process proceeds to step S15.

[0049] In step S13, the rotation speed of the refrigerant pump 12 is reduced by a predetermined small amount. Then, in step S14, step S13 is repeatedly executed until the temperature Ta becomes greater than T2d (Yes), and if the temperature Ta becomes smaller than T2d (No), the process proceeds to step S16.

[0050] As described above, in the ejector type cooling device 10A, the control unit adjusts the opening of the flow rate control valve 26 to maintain the temperature Ta detected by the first temperature detector 30 within the range of ΔT1. Furthermore, the opening of the expansion valve 22 is adjusted to finely adjust the temperature Ta, so that the detected temperature Ta is more reliably maintained within the range of ΔT1. Also, in FIG. 3B, when the temperature Ta is lower than T2d even with the flow rate control valve 26 fully closed, the rotation speed of the refrigerant pump 12 is reduced to suppress the cooling capacity of the system and raise the temperature Ta to an appropriate temperature by the processing of steps S12 to S14.

[0051] The temperature control procedure for adjusting the cooling water temperature Ta to an appropriate temperature is not limited to the one shown in Figures 3A and 3B, and may be a one-stage threshold control omitting the control procedure based on ΔT2, and may be a two-stage threshold control based on ΔT1 and ΔT2 as shown in Figure 4. In addition, when an optimal value is assumed according to the capacity of the evaporator 20, the opening degree of the expansion valve 22 may be searched for and determined. In the control shown in Figures 3A and 3B, the control unit controls the flow rate adjustment valve 26, the refrigerant pump 12, and the expansion valve 22 to adjust the temperature Ta, but may control at least one of the refrigerant pump 12 and the expansion valve 22 in addition to the flow rate adjustment valve 26.

[0052] As described above, the ejector-type cooling device 10A includes the auxiliary heat exchanger 24 that cools the hot water between the steam generator 14 and the evaporator 20 connected in series, thereby improving the cooling capacity and enabling the temperature Ta of the output hot water W2 to be further reduced. Therefore, even if the temperature of the hot water W1 supplied is relatively high due to the specifications of the connected production device 11 or seasonal factors, the temperature Ta can be controlled to be within a predetermined range.

[0053] FIG. 5 is a circuit diagram showing the configuration of an ejector-type cooling device 10B according to the second embodiment. In the ejector-type cooling device 10B, the auxiliary heat exchanger 24 in the ejector-type cooling device 10A is replaced with a heat dissipation means (auxiliary cooler) 34, and the flow rate control valve 26 is omitted. The heat dissipation means 34 is interposed between the steam generator 14 and the evaporator 20, and has a radiator 34a through which hot water flows, and a fan (cooling adjustment unit) 34b that blows air to the radiator 34a. In other words, the heat dissipation means 34 is a so-called forced air-cooled radiator. The radiator 34a is provided with many fins to ensure a large surface area, and can dissipate heat from the hot water flowing inside. When the heat dissipation means 34 is used, cooling water for the auxiliary cooler is not required. The radiator 34a may be replaced with, for example, a heat sink.

[0054] The fan 34b is controlled by the control unit to have its rotation speed or be on / off controlled, and air-cools the radiator 34a to promote heat dissipation. If it is not necessary to dissipate heat from the hot water, the heat dissipation means 34 may be bypassed by a bypass switching circuit (not shown). The temperature Ta in the ejector-type cooling device 10B can be controlled by replacing the opening control of the flow rate adjustment valve 26 with the rotation speed control of the fan 34b in the procedure shown in Figures 3A and 3B.

[0055] FIG. 6 is a circuit diagram showing the configuration of an ejector-type cooling device 10C according to a third embodiment. The ejector-type cooling device 10C is obtained by inserting a heat dissipation means 34 in series between the auxiliary heat exchanger 24 and the evaporator 20 in the above-mentioned ejector-type cooling device 10A. The heat dissipation means 34 is the same as that shown in FIG. 5. The arrangement of the auxiliary heat exchanger 24 and the heat dissipation means 34 may be reversed. The control of the temperature Ta in the ejector-type cooling device 10C may be performed by executing the opening control of the flow rate adjustment valve 26 and the rotation speed control of the fan 34b in parallel in the procedure shown in FIG. 3A and FIG. 3B, or by executing one of them complementarily to the other. The ejector-type cooling devices 10B and 10C also have the same effects as the above-mentioned ejector-type cooling device 10A.

[0056] Thus, the auxiliary cooling device provided between the steam generator 14 and the evaporator 20 may include both the auxiliary heat exchanger 24 and the heat dissipation means 34 (ejector-type cooling device 10C), may include only the steam generator 14 (ejector-type cooling device 10A), may include only the heat dissipation means 34 (ejector-type cooling device 10B), or may be provided with other cooling means.

[0057] The ejector-type cooling device 10 may be used for any purpose, including consumer use, industrial use, etc. The present invention is not limited to the above-described embodiment, and can of course be freely modified without departing from the spirit and scope of the present invention. [Explanation of symbols]

[0058] 10, 10A, 10B, 10C Ejector type cooling device 12 Refrigerant pump 14 Steam Generator 16 Ejector 18 Condenser 20 Evaporator 22 Expansion valve 24 Auxiliary heat exchanger (auxiliary cooler) 26 Flow rate control valve (cooling control part) 30 First temperature detector 32 Second temperature detector 34 Heat radiation means (auxiliary cooler, forced air cooling type radiator) B1, B2 branch J Confluence Ta,Tb temperature

Claims

1. a condenser that condenses the gas phase refrigerant by heat exchange with cooling water; a refrigerant pump that pressurizes and circulates the refrigerant condensed in the condenser; a steam generator that receives the refrigerant discharged from the refrigerant pump and evaporates the refrigerant by heat exchange with hot water; an evaporator connected in series with the steam generator so that hot water flows downstream of the steam generator, and a refrigerant is supplied from a branch portion between the condenser and the refrigerant pump through an expansion valve and evaporates by exchanging heat with the hot water; an ejector connected to supply the refrigerant evaporated in the vapor generator to a driving flow port, supply the refrigerant from a discharge port to the condenser, and further to draw the refrigerant supplied from the evaporator through a suction port; an auxiliary cooler for cooling hot water between the steam generator and the evaporator connected in series; An ejector type cooling device comprising:

2. A cooling adjustment unit that adjusts the capacity of the sub-cooler to cool the hot water; a first temperature detector for detecting a temperature of hot water flowing out from the evaporator; a control unit that controls the cooling adjustment unit so that the detected temperature of the first temperature detector is within a predetermined temperature range; 2. The ejector type cooling device according to claim 1, further comprising:

3. The auxiliary cooler includes an auxiliary heat exchanger to which a portion of the cooling water is supplied and which exchanges heat with hot water, 3. The ejector type cooling device according to claim 2, wherein the cooling adjustment unit is a flow rate adjustment valve that adjusts the flow rate of the cooling water supplied to the auxiliary heat exchanger.

4. The auxiliary cooler includes a forced air-cooled radiator; 4. The ejector type cooling device according to claim 2, wherein the cooling adjustment unit is a fan that blows air to the forced air-cooling radiator.

5. The ejector-type cooling device according to any one of claims 2 to 4, characterized in that the control unit further controls at least one of the expansion valve and the refrigerant pump so that the detected temperature of the first temperature detector is within a predetermined temperature range.

6. a second temperature detector for detecting a temperature of the refrigerant flowing into the evaporator; The ejector-type cooling device according to any one of claims 2 to 5, characterized in that the control unit increases the opening of the expansion valve by a predetermined small amount when the temperature difference between the detected temperature of the first temperature detector and the detected temperature of the second temperature detector is equal to or greater than a predetermined threshold, and decreases the opening of the expansion valve by a predetermined small amount when the temperature difference is smaller than the predetermined threshold.

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