JP2012017926A - Steam system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a steam system compatible with a change of a use load of steam, which can supply steam having stable steam pressure to steam use equipment, even if there is a difference between steam pressure from a heat pump and steam pressure from a boiler.SOLUTION: In the heat pump 2, a compressor 5, a condenser 6, an expansion valve 7 and an evaporator 8 are sequentially and annularly connected to one another to circulate a refrigerant, and steam is generated in the condenser 6 by heat-exchanging the refrigerant and water. By injecting the steam output from the boiler 3 from a nozzle 16, an executer 4 sucks the steam from the condenser 6 and discharges it by mixing it with the steam from the nozzle 16. A first sensor 25 detects steam at the outlet side of the executer 4, and a second sensor 26 detects the pressure of steam to a suction part 18 of the executer 4. The supply of steam to the nozzle 16 is controlled on the basis of a detection value of the first sensor 25, and the compressor 5 is controlled on the basis of a detection value of the second sensor 26.

Description

  The present invention relates to a steam system including one or both of a heat pump and a steam compressor, and a boiler.

  Conventionally, as disclosed in Patent Document 1 below, a steam system (S1) including a heat pump (10), a steam compressor (30), and an exhaust gas boiler (130) has been proposed.

JP 2008-45807 A

  However, in the prior art, as described in [0025], the steam compressor (30) is controlled based on the pressure in the tank (47). Therefore, the amount of steam from the steam compressor (30) and the amount of steam from the exhaust gas boiler (130) cannot be adjusted according to changes in the steam usage load in the steam-using facility. Further, when there is a difference between the steam pressure from the steam compressor (30) and the steam pressure from the exhaust gas boiler (130), there is no means for correcting this.

  The problem to be solved by the present invention is to provide a steam system that can cope with a change in the use load of steam. It is another object of the present invention to make it possible to supply steam having a stable vapor pressure to a steam-using facility even if there is a difference between the vapor pressure from a heat pump or a steam compressor and the vapor pressure from a boiler.

  The present invention has been made to solve the above problems, and the invention according to claim 1 includes a heat pump or a vapor compressor, an ejector, a first sensor, and a second sensor, A compressor, a condenser, an expansion valve, and an evaporator are sequentially connected in an annular manner to circulate the refrigerant. In the condenser, heat is exchanged between the refrigerant and water to generate steam, and the steam compressor The ejector sucks the steam from the condenser or the steam compressor by ejecting the steam from the boiler from the nozzle, and mixes and discharges the steam with the steam from the nozzle. The first sensor detects the pressure of the steam on the outlet side of the ejector, the second sensor detects the pressure of the steam to the suction portion of the ejector, and based on the detection value of the first sensor The nozzle Controls for feeding steam, a steam system, wherein the controller controls the compressor or the vapor compressor based on a detection value of the second sensor.

  According to invention of Claim 1, the vapor | steam from a condenser or a vapor | steam compressor can be pressure | voltage-risen with an ejector, and can be supplied to a vapor | steam utilization equipment. Therefore, compared with the case where there is no pressure increase in the ejector, the vapor pressure at the outlet of the condenser or the steam compressor can be lowered, thereby improving the efficiency of the heat pump and preventing the enlargement of the heat pump or the steam compressor. Can be. In addition, it is possible to supply steam according to changes in the steam use load to the steam using facility.

  The invention according to claim 2 controls a steam supply valve provided in a steam supply path to the nozzle and / or changes a size of a nozzle portion of the nozzle based on a detection value of the first sensor. The steam system according to claim 1, wherein a throat adjustment mechanism is controlled.

  According to the second aspect of the present invention, the steam supply to the nozzle of the ejector, and thus the operation of the ejector, can be controlled using the steam supply valve and / or the throat adjustment mechanism.

  Invention of Claim 3 is provided with the bypass path which connects the steam supply path to the said nozzle and the exhaust steam path from the said ejector, and the bypass valve provided in this bypass path, The steam supply path to the said nozzle In the case where the steam supply valve is provided, the bypass path is provided so as to branch from the upstream side of the steam supply valve, and the steam supply valve or the node adjustment mechanism is configured to detect the detection value of the first sensor. The bypass valve is controlled to be maintained at a first set value, and the opening and closing or opening degree of the bypass valve is adjusted to maintain the pressure downstream thereof at the second set value, and the second set value is the first set value The steam system according to claim 2, wherein the steam system is set lower than the value.

  According to the third aspect of the present invention, steam from the heat pump or the steam compressor to the steam via the ejector and the steam from the boiler via the bypass valve can be supplied to the steam using facility without passing through the ejector. . Thereby, steam can be stably supplied to the steam-using facility. Moreover, by setting the set pressure of the bypass valve lower than the control pressure of the ejector, the steam supply from the heat pump or the steam compressor via the ejector can be given priority over the steam supply from the boiler via the bypass valve. it can.

  Invention of Claim 4 is equipped with both the said heat pump and the said vapor | steam compressor, the said vapor | steam compressor suck | inhales, compresses and discharges | emits the vapor | steam from the said condenser, The said ejector is from the said boiler. By ejecting steam from the nozzle, the steam from the steam compressor is sucked, mixed with the steam from the nozzle and discharged, and the steam compressor is controlled based on the detection value of the second sensor. 4. The compressor according to claim 1, wherein the compressor is controlled based on a pressure of a refrigerant in the condenser or a pressure of steam sent from the condenser to the steam compressor. 5. It is a steam system.

  According to the fourth aspect of the present invention, the steam generated by the heat pump can be boosted by the steam compressor and supplied to the suction portion of the ejector. In addition, the operation of the ejector can be stabilized by controlling the pressure on the suction portion side of the ejector as a reference.

  The invention according to claim 5 includes a third sensor in place of or in addition to the second sensor, and the third sensor is a pressure or temperature of the fluid passed through or passed through the evaporator. Or the pressure or temperature of the fluid on the inlet side of the steam compressor is detected, and the compressor or the steam compressor is controlled based on a detection value of the third sensor. 4. The steam system according to any one of 3 above.

  According to the fifth aspect of the present invention, the heat pump and the steam compressor can be controlled based on the pressure or temperature of the heat source fluid of the heat pump or the pressure or temperature of the fluid on the inlet side of the steam compressor. Thereby, for example, the fluid passed through the evaporator can be cooled to a desired temperature.

  Invention of Claim 6 is equipped with both the said heat pump and the said vapor | steam compressor, the said vapor | steam compressor suck | inhales, compresses and discharges | emits the vapor | steam from the said condenser, The said ejector is from the said boiler. By ejecting steam from the nozzle, the steam from the steam compressor is sucked, mixed with the steam from the nozzle and discharged, and the compressor is controlled based on the detection value of the third sensor, The steam system according to claim 5, wherein the steam compressor is controlled based on a pressure of a refrigerant in the condenser or a pressure of steam sent from the condenser to the steam compressor.

  According to the sixth aspect of the present invention, the steam generated by the heat pump can be boosted by the steam compressor and supplied to the suction portion of the ejector. In addition, the pressure or temperature can be adjusted by controlling the pressure or temperature of the heat source fluid of the heat pump as a reference.

The invention according to claim 7 is based on the detection value of the second sensor, the range of the third upper limit value and the third lower limit value, and the third upper limit value as a set value, the compressor or the steam Proportional control or PID control of the compressor, or a range between a fourth upper limit value and a fourth lower limit value based on a detection value of the third sensor, and the fourth lower limit value as a set value, the compressor or Proportional control or PID control of the steam compressor is performed, and a first deviation rate and a second deviation rate are obtained by the following equations based on a current value by each sensor at a set timing. 6. The steam system according to claim 5, wherein the control is performed with a smaller deviation rate among the control by the sensor.
First deviation rate = (third upper limit value−current value) / (third upper limit value−third lower limit value)
Second deviation rate = (current value−fourth lower limit value) / (fourth upper limit value−fourth lower limit value)

  The smaller the deviation rate is, the closer to the target value, the smaller the operation amount of the compressor or the steam compressor. If an attempt is made to control a compressor or a steam compressor with a larger deviation rate, that is, a larger manipulated variable, the smaller deviation rate, that is, the smaller manipulated value, will soon reach the target value. become. However, according to the seventh aspect of the invention, the frequency at which the compressor or the steam compressor stops can be reduced by appropriately switching to the control with the smaller deviation rate. Moreover, even if it stops, it can transfer to a stop state gradually. Furthermore, there is no need to manually set pressure control or temperature control.

  The invention according to claim 8 is based on the detection value of the second sensor, is in the range between the third upper limit value and the third lower limit value, and the third upper limit value as a set value, and the compressor or the steam Proportional control or PID control of the compressor, or a range between a fourth upper limit value and a fourth lower limit value based on a detection value of the third sensor, and the fourth lower limit value as a set value, the compressor or Proportional control or PID control of the steam compressor, based on a current value by each sensor at a set timing, an operation amount of the compressor or the steam compressor in control by the second sensor, and control by the third sensor 6. The operation amount of the compressor or the steam compressor is obtained, and control is performed with the smaller operation amount of the control by the second sensor and the control by the third sensor. Description A steam system.

  If an attempt is made to control the compressor or the steam compressor with a larger operation amount, the smaller operation amount immediately reaches the target value. However, according to the eighth aspect of the invention, the frequency at which the compressor or the steam compressor stops can be reduced by appropriately switching to the control with the smaller operation amount. Moreover, even if it stops, it can transfer to a stop state gradually. Furthermore, there is no need to manually set pressure control or temperature control.

The invention according to claim 9 includes both the heat pump and the steam compressor, the steam compressor sucks, compresses and discharges the steam from the condenser, and the ejector is supplied from the boiler. By ejecting steam from the nozzle, the steam from the steam compressor is sucked, mixed with the steam from the nozzle and discharged, and the refrigerant pressure of the condenser or the steam compression from the condenser is discharged. A fourth sensor for detecting the pressure of the steam sent to the machine, based on the detection value of the second sensor, in the range between the third upper limit value and the third lower limit value, and the third upper limit value as a set value The steam compressor is proportionally controlled or PID controlled, or based on the detection value of the third sensor, in a range between a fourth upper limit value and a fourth lower limit value, and the fourth lower limit value as a set value, Compressor proportional control or PID If the steam compressor is controlled based on the detection value of the second sensor, the compressor is controlled based on the detection value of the fourth sensor, and the compressor is controlled based on the detection value of the third sensor. When controlling, control the steam compressor based on the detection value of the fourth sensor, based on the current value by each sensor at the set timing, to determine the first deviation rate and the second deviation rate by the following formula, 6. The steam system according to claim 5, wherein control is performed with a smaller deviation rate of control by the second sensor and control by the third sensor.
First deviation rate = (third upper limit value−current value) / (third upper limit value−third lower limit value)
Second deviation rate = (current value−fourth lower limit value) / (fourth upper limit value−fourth lower limit value)

  According to the ninth aspect of the present invention, the steam generated by the heat pump can be boosted by the steam compressor and supplied to the suction portion of the ejector. In this case, the control by the second sensor and the control by the third sensor can be appropriately switched according to the deviation rate.

  Furthermore, the invention described in claim 10 includes both the heat pump and the steam compressor, the steam compressor sucks, compresses and discharges the steam from the condenser, and the ejector includes the boiler. The steam from the nozzle is sucked out from the steam compressor, mixed with the steam from the nozzle and discharged, and the pressure of the refrigerant in the condenser or the condenser from the condenser is discharged. A fourth sensor for detecting the pressure of the steam sent to the steam compressor is provided, and the third upper limit value is set in a range between the third upper limit value and the third lower limit value based on the detection value of the second sensor. As a value, the steam compressor is proportionally controlled or PID controlled, or based on a detection value of the third sensor, a range between a fourth upper limit value and a fourth lower limit value, and the fourth lower limit value as a set value , Proportional control of the compressor Is PID-controlled, and when the steam compressor is controlled based on the detection value of the second sensor, the compressor is controlled based on the detection value of the fourth sensor, and the compression is controlled based on the detection value of the third sensor. When controlling the machine, the steam compressor is controlled based on the detection value of the fourth sensor, and at a set timing, the first operation amount (y1) of the steam compressor in the control by the second sensor, and the second A value (y1 / y2) of the ratio of the first operation amount (y1) to the second operation amount (y2) is obtained from the second operation amount (y2) of the compressor in the control by three sensors, and this value 6. The steam system according to claim 5, wherein control is performed by the second sensor if is less than a preset constant, and control by the third sensor is performed if the constant is equal to or greater than the constant.

  According to invention of Claim 10, the vapor | steam generated with the heat pump can be pressure | voltage-risen with a steam compressor, and can be supplied to the suction part of an ejector. In this case, the control by the second sensor and the control by the third sensor can be appropriately switched according to the operation amount.

  ADVANTAGE OF THE INVENTION According to this invention, the vapor | steam system which can respond to the change of the usage load of a vapor | steam is realizable. Moreover, even if there is a difference between the steam pressure from the heat pump or the steam compressor and the steam pressure from the boiler, by using the ejector, steam having a stable steam pressure can be supplied to the steam using facility.

It is the schematic which shows Example 1 of the steam system of this invention. It is the schematic which shows the correspondence of the detection pressure of a 1st sensor, the opening / closing state of a steam supply valve, and the opening / closing state of a bypass valve. It is a figure which shows the modification of FIG. It is the schematic which shows the correspondence of the detection pressure of a 2nd sensor, and the operation state of a compressor. It is a figure which shows the modification of FIG. It is the schematic which shows the correspondence of the detection pressure or detection temperature of a 3rd sensor, and the operation state of a compressor. It is a figure which shows the modification of FIG. It is the schematic which shows Example 2 of the steam system of this invention. It is the schematic which shows Example 3 of the steam system of this invention. It is the schematic which shows Example 4 of the steam system of this invention.

  Hereinafter, specific embodiments of the present invention will be described in detail with reference to the drawings.

FIG. 1 is a schematic diagram showing Example 1 of the steam system of the present invention.
The steam system 1 of this embodiment includes a heat pump 2, a boiler 3, and an ejector 4.

  The heat pump 2 is a vapor compression heat pump, and includes a compressor 5, a condenser 6, an expansion valve 7, and an evaporator 8 that are sequentially connected in an annular shape. The compressor 5 compresses the gas refrigerant to a high temperature and a high pressure. The condenser 6 condenses and liquefies the gas refrigerant from the compressor 5. Further, the expansion valve 7 allows the liquid refrigerant from the condenser 6 to pass therethrough, thereby reducing the pressure and temperature of the refrigerant. The evaporator 8 evaporates the refrigerant from the expansion valve 7.

  Therefore, in the heat pump 2, the refrigerant takes heat from the outside in the evaporator 8 and vaporizes, while in the condenser 6, the refrigerant dissipates heat to the outside and condenses. By using this, the heat pump 2 uses the evaporator 8 to supply hot water (for example, exhausted hot water discharged from a factory or the like), air (heated air such as air discharged from an air compressor, as well as outside air). Heat) from exhaust gas or the like, and in the condenser 6, water is heated to generate steam. The feed water to the condenser 6 is preferably pure water or soft water in order to prevent adhesion of scale (deposited in water) to the heat exchanger constituting the condenser 6.

  The refrigerant used for the heat pump 2 is not particularly limited, but is a hydrofluorocarbon (HFC) having 4 or more carbon atoms or a mixture obtained by adding water and / or a fire extinguishing liquid, alcohol (for example, ethyl alcohol or methyl alcohol) or water And what added fire extinguishing liquid, or water (for example, pure water or soft water) is used suitably.

  The heat pump 2 is not limited to a single stage and may be a plurality of stages. Even when the heat pump 2 has a plurality of stages, the heat pumps 2 constituting each stage are basically the same as the single stage heat pump 2 shown in FIG. When the heat pump 2 has a plurality of stages, the adjacent heat pumps 2 and 2 may be connected using an indirect heat exchanger or may be connected using a direct heat exchanger (intercooler). Good. In the former case, an indirect heat exchanger is provided that receives the refrigerant from the compressor 5 of the lower heat pump 2 and the refrigerant from the expansion valve 7 of the upper heat pump 2 and exchanges heat without mixing both refrigerants. The condenser is the condenser 6 of the lower heat pump 2 and the evaporator 8 of the upper heat pump 2. On the other hand, in the latter case, an intermediate cooler that receives the refrigerant from the compressor 5 of the lower heat pump 2 and the refrigerant from the expansion valve 7 of the upper heat pump 2 and directly exchanges heat between the two refrigerants is provided. The intermediate cooler is the condenser 6 of the lower heat pump 2 and the evaporator 8 of the upper heat pump 2.

  Thus, the multi-stage (multi-stage) heat pump 2 includes a multi-element (multi-element) heat pump, a single-element multi-stage heat pump, or a combination thereof. In any case, when the heat pump 2 has a plurality of stages, the evaporator 8 of the lowermost heat pump 2 draws heat from the outside, and the condenser 6 of the uppermost heat pump 2 warms water to generate steam. Let Hereinafter, unless otherwise specified, when simply referring to the evaporator 8, when the heat pump 2 has a plurality of stages, it refers to the evaporator 8 of the lowermost heat pump 2, and when simply referred to as the condenser 6, the heat pump 2 includes a plurality of stages. Is the condenser 6 of the uppermost heat pump 2.

  In the single-stage heat pump 2 or a part or all of the heat pumps 2 in the multi-stage heat pump 2, the refrigerant from the condenser 6 to the expansion valve 7 and the refrigerant from the evaporator 8 to the compressor 5 are not mixed. A liquid gas heat exchanger (not shown) for heat exchange may be provided. By providing the liquid gas heat exchanger, the refrigerant from the evaporator 8 to the compressor 5 is superheated by the refrigerant from the condenser 6 to the expansion valve 7. Thus, the coefficient of performance (COP) of the heat pump 2 can be increased by increasing the enthalpy on the inlet side of the compressor 5 and thereby increasing the enthalpy on the outlet side of the compressor 5. In addition, the disadvantage that the liquid refrigerant is supplied to the compressor 5 can be prevented. However, in the case of the multi-stage heat pump 2, it is better not to provide the liquid gas heat exchanger in the uppermost heat pump 2. By not providing a liquid gas heat exchanger in the uppermost heat pump 2 that is high temperature and pressure, temperature rise on the outlet side of the compressor 5 can be prevented, and deterioration of the lubricating oil of the compressor 5 can be prevented. Can do.

  In the single-stage heat pump 2 or the uppermost heat pump 2 of the multiple-stage heat pumps 2, a subcooler 9 may be provided between the condenser 6 and the expansion valve 7 as desired. The subcooler 9 is an indirect heat exchanger that exchanges heat without mixing the refrigerant from the condenser 6 to the expansion valve 7 and the feed water to the condenser 6. The subcooler 9 can supercool the refrigerant from the condenser 6 to the expansion valve 7 with the water supplied to the condenser 6, and can supply the water to the condenser 6 with the refrigerant from the condenser 6 to the expansion valve 7. Can be warmed. Further, the heat exchange between the refrigerant and water can be divided into the subcooler 9 as a heat exchange part by sensible heat and the condenser 6 as a heat exchange part mainly by latent heat, so that the heat transfer efficiency can be improved.

  When both the liquid gas heat exchanger and the subcooler 9 are provided, the refrigerant from the condenser 6 may pass through the liquid cooler 9 after passing through the liquid gas heat exchanger, or the liquid gas heat exchanger after passing through the subcooler 9. Or through the liquid gas heat exchanger and the subcooler 9 in parallel.

  The compressor 5 includes a compressor body and a drive device for the compressor, and the drive device includes an engine (typically a gas engine or a diesel engine) and / or a motor. As a specific aspect of the control of the compressor 5, for example, the drive device is on / off controlled. Alternatively, a power transmission device (clutch and / or transmission) from the drive device to the compressor main body is provided between the compressor main body and the drive device, and whether or not power is transmitted from the drive device to the compressor main body, The power transmission device is controlled to change the amount. Or the motor which comprises a drive device is controlled by an inverter, and the rotation speed (it can also be said to be a rotational speed) of a motor is changed. Alternatively, the engine output constituting the drive device is controlled to change the engine output. Alternatively, the compressor main body is controlled in order to mechanically adjust the refrigerant discharge flow rate (including the case where the discharge flow rate is changed by adjusting the suction side) of the compressor main body. Of these, a plurality of them may be combined to control the compressor 5. In addition, when using a motor as a drive device, you may drive a motor with the electric power of SOFC (solid oxide fuel cell) mentioned later.

  As long as the condenser 6 is configured to exchange heat without mixing refrigerant and water, the specific configuration thereof is not particularly limited. For example, a plate heat exchanger or a shell and tube heat exchanger is used. Similarly, the evaporator 8 may have any specific configuration as long as heat is exchanged without mixing the heat source fluid such as warm water, air, or exhaust gas and the refrigerant of the heat pump 2.

  Water can be supplied to the condenser 6 via the water supply channel 10, and a desired amount of water is stored in the condenser 6. In the present embodiment, the water supply passage 10 is provided with a water supply pump 11, a water supply valve 12, a check valve 13, and a subcooler 9 as required. Water is supplied to the condenser 6 through these in order. In this case, the opening / closing of the water supply valve 12 may be controlled based on the water level in the condenser 6 with the water supply pump 11 being operated. For example, the water supply valve 12 may be opened when the lower limit water level is reached, and the water supply valve 12 may be closed when the upper limit water level is reached. However, instead of omitting the installation of the water supply valve 12, the water supply pump 11 is inverter-controlled using a capacitance type water level detector capable of obtaining a signal proportional to the water level, and the desired value is stored in the condenser 6. An amount of water may be stored.

  The boiler 3 is typically a fuel-fired boiler or an electric boiler. A fuel-fired boiler is a device that vaporizes water by burning fuel, and the presence or amount of combustion is adjusted so as to maintain the vapor pressure as desired. The electric boiler is a device that vaporizes water with an electric heater, and the presence or amount of power supply to the electric heater is adjusted so as to maintain the vapor pressure as desired.

  However, the boiler 3 is not limited to a fuel-fired boiler or an electric boiler, and may be a waste heat boiler. A waste heat boiler is a device that vaporizes water using waste heat, and the presence or amount of waste heat supplied to the waste heat boiler can be adjusted so that the steam pressure is maintained as desired. Good. In the case of the waste heat boiler, the heat source is not particularly limited, and for example, exhaust gas from the engine of the compressor 5 or waste heat from the SOFC (solid oxide fuel cell) can be used.

  The first steam path 14 from the boiler 3 and the second steam path 15 from the condenser 6 are configured to merge via the ejector 4. As is well known, the ejector 4 includes a nozzle 16 and a diffuser 17, and by sucking low-pressure steam from the suction unit 18 by jetting high-pressure steam from the nozzle 16 toward the diffuser 17, the both steam are mixed. To discharge. Here, the first steam path 14 is connected to the nozzle 16, and the second steam path 15 is connected to the suction part 18. Therefore, the first steam path 14 can be referred to as a steam supply path to the nozzle 16, and the second steam path 15 can be referred to as a suction path to the ejector 4.

  Since it is such a structure, the vapor | steam from the condenser 6 is attracted | sucked by the ejector 4 by the vapor | steam from the boiler 3 being blown in to the nozzle 16. FIG. Both steams are mixed and discharged from the ejector 4 to the third steam path 19. Therefore, it can be said that the third steam path 19 is an exhaust steam path from the ejector 4.

  In the ejector 4, the steam from the first steam path 14 is depressurized, while the steam from the second steam path 15 is pressurized. Then, the steam in the third steam path 19 is sent to one or a plurality of various steam use facilities 20 (FIG. 10).

  The presence / absence and amount of vapor jet from the nozzle 16 can be adjusted. For example, a steam supply valve 21 is provided in the first steam path 14, and the opening / closing or opening degree of the steam supply valve 21 can be adjusted. Alternatively, the throat adjustment mechanism 22 is provided so that the size of the throat of the nozzle 16 can be changed, and by operating the throat adjustment mechanism 22, the presence or amount of steam passing through the throat can be adjusted. The specific configuration of the throat adjustment mechanism 22 is not particularly limited. For example, like a needle valve, the throat adjustment mechanism 22 is configured to be able to change the cross-sectional area of the throat by moving the needle forward and backward with respect to the throat of the nozzle 16. Of these, a plurality of them may be combined to control the steam supply to the nozzle 16.

  The first steam path 14 and the third steam path 19 are connected via the ejector 4 and preferably also connected via the bypass path 23. When the steam supply valve 21 is provided in the first steam path 14, the first steam path 14 upstream of the steam supply valve 21 and the third steam path 19 are connected by the bypass path 23.

  A bypass valve 24 is provided in the bypass path 23. In the present embodiment, the bypass valve 24 is a self-reducing pressure reducing valve (secondary pressure regulating valve). The upstream side of the bypass valve 24 is maintained at a higher pressure by the boiler 3 than the downstream side.

  A first sensor 25 including a pressure sensor is provided at a position where the pressure of the combined steam of the steam from the ejector 4 and the steam from the bypass valve 24 can be detected. In the illustrated example, the first sensor 25 is provided on the upstream side of the third steam path 19 where the bypass path 23 is connected, but on the downstream side of the position where the bypass path 23 is connected. Alternatively, it may be provided on the downstream side of the bypass valve 24 in the bypass passage 23. Moreover, when the steam from the ejector 4 and the steam from the bypass path 23 are merged by the steam header, the first sensor 25 may be provided in the steam header.

  The second sensor 26 including a pressure sensor is also provided in the second steam path 15. The second sensor 26 detects the pressure of the steam generated in the condenser 6, in other words, the pressure of the steam sucked into the ejector 4.

  A heat source fluid such as hot water, air, or exhaust gas is passed through the evaporator 8, and the supply path 27 of the heat source fluid to the evaporator 8 or the discharge path 28 from the evaporator 8 is supplied from a pressure sensor or a temperature sensor. A third sensor 29 is provided. For example, when it is intended to cool the warm water in the evaporator 8, it is preferable to provide a third sensor 29 including a temperature sensor in the discharge path 28 from the evaporator 8.

  In the present embodiment, the steam supply valve 21 and / or the throat adjustment mechanism 22 are controlled based on the detection value of the first sensor 25. Furthermore, the compressor 5 is controlled based on the detection value of one or both of the second sensor 26 and the third sensor 29. In addition, installation and control of one of the steam supply valve 21 and the throat adjusting mechanism 22 can be omitted as appropriate. In the following, a case will be described in which the installation of the throat adjustment mechanism 22 is omitted and the steam supply valve 21 is controlled, but the throat adjustment mechanism 22 is installed and replaced with or in addition to the control of the steam supply valve 21. Thus, the throat adjustment mechanism 22 may be similarly controlled.

  Hereinafter, (1) control by the first sensor 25, (2) control by the second sensor 26, (3) control by the third sensor 29, and (4) switching control between the second sensor 26 and the third sensor 29. These will be described in order. Among these, the control by the first sensor 25 can be performed in parallel with the control by the second sensor 26 and the control by the third sensor 29. When the control by the second sensor 26 is performed, the installation of the third sensor 29 can be omitted if desired. Conversely, when the control by the third sensor 29 is performed, the second sensor 26 can be performed as desired. Can be omitted.

<(1) Control by first sensor 25>
FIG. 2 is a schematic diagram showing a correspondence relationship between the detected pressure of the first sensor 25, the open / close state of the steam supply valve 21, and the open / close state of the bypass valve 24. Here, the steam supply valve 21 is opened and closed at a first set value (first set pressure) P1, and the bypass valve 24 is opened and closed at a second set value (second set pressure) P2.

  Specifically, when the pressure on the downstream side of the bypass valve 24 is less than the second set value P2, both the steam supply valve 21 and the bypass valve 24 are open. Thereby, the steam from the ejector 4 and the bypass path 23 is supplied to the steam use facility 20. When the second set value P2 or more is reached, the bypass valve 24 is closed, the steam supply from the bypass passage 23 is stopped, and the steam is supplied from the ejector 4. When the detected pressure of the first sensor 25 becomes equal to or higher than the first set value P1, the steam supply valve 21 is closed, and the supply of steam from the ejector 4 is also stopped. When the detected pressure of the first sensor 25 becomes less than the first set value P1, the steam supply valve 21 is opened and the ejector 4 is actuated. Thereafter, the steam from the ejector 4 cannot be covered by the second set value. When it becomes less than P2, the bypass valve 24 is opened and steam is also supplied from the bypass passage 23. When the bypass valve 24 is a self-reducing pressure reducing valve, the bypass valve 24 mechanically performs these operations.

  Needless to say, a differential (operation gap) is set for each of the first set value P1 and the second set value P2. Moreover, the opening degree of the steam supply valve 21 may be adjusted not only by opening and closing but also by proportional control or PID control. Further, the bypass valve 24 may be configured by an electromagnetic valve or an electric valve. In that case, the bypass valve 24 may be opened and closed based on the detected pressure of the first sensor 25, or the opening degree is adjusted by proportional control or PID control. Also good.

  These cases will be described with reference to FIG. In FIG. 3, the differential (or proportional band) P1H to P1L of the first set value P1 and the differential (or proportional band) P2H to P2L of the second set value P2 do not overlap, but part of them. You may overlap. That is, the second upper limit pressure P2H may be set higher than the first lower limit pressure P1L.

  First, on / off control in which a differential is set for each of the first set value P1 and the second set value P2 will be described. In this case, with respect to the first set value P1, the first upper limit pressure P1H and the first lower limit pressure P1L are set, and the steam supply valve when the detected pressure of the first sensor 25 becomes equal to or higher than the first upper limit pressure P1H when the pressure rises. When 21 is closed and the pressure detected by the first sensor 25 falls below the first lower limit pressure P1L, the steam supply valve 21 is opened. For the second set value P2, the second upper limit pressure P2H and the second lower limit pressure P2L are set. When the pressure rises, the bypass valve 24 closes when the pressure exceeds the second upper limit pressure P2H, and when the pressure drops, When the pressure is less than the second lower limit pressure P2L, the bypass valve 24 is opened.

  Next, an example of proportional control of the steam supply valve 21 and the bypass valve 24 will be described. In this case, based on the detected pressure of the first sensor 25, the steam supply valve 21 is proportional in the range between the first upper limit pressure P1H and the first lower limit pressure P1L and with the first upper limit pressure P1H as a set value (target value). Control. Further, based on the detected pressure of the first sensor 25, the bypass valve 24 is proportionally controlled in the range between the second upper limit pressure P2H and the second lower limit pressure P2L and with the second upper limit pressure P2H as a set value (target value). . Here, at the first upper limit pressure P1H or higher, the steam supply valve 21 is fully closed, and when it is less than the first lower limit pressure P1L, the steam supply valve 21 is fully opened. Further, the bypass valve 24 is fully closed at the second upper limit pressure P2H or higher, and the bypass valve 24 is fully opened at the pressure lower than the second lower limit pressure P2L. Note that PID control may be performed instead of proportional control.

  In any case, by setting the second set value P2 lower than the first set value P1, the steam supply facility 20 is given priority to the steam supply from the ejector 4, in other words, the steam supply from the heat pump 2. Steam can be supplied stably. That is, while giving priority to the supply of steam from the ejector 4, the steam from the bypass path 23 can be sent to the steam using facility 20 when this is not sufficient.

<(2) Control by the second sensor 26>
FIG. 4 is a schematic diagram showing a correspondence relationship between the detected pressure of the second sensor 26 and the operating state of the compressor 5. Here, the compressor 5 is turned on / off at a third set value (third set pressure) P3. Specifically, if the detected pressure of the second sensor 26 is less than the third set value P3, the compressor 5 is driven and steam is generated by the heat pump 2, while the detected pressure of the second sensor 26 is the third pressure. If it becomes more than preset value P3, compressor 5 will be stopped and the generation of steam from heat pump 2 will be stopped.

  Needless to say, a differential (operation gap) is set as desired in the third set value P3. Further, the compressor 5 may be proportionally controlled or PID controlled by adjusting the rotational speed, for example, instead of on / off control of driving and stopping thereof. This case will be described with reference to FIG. In FIG. 5, the range between the third upper limit pressure P3H and the third lower limit pressure P3L is the differential or proportional band of the third set value P3.

  First, the on / off control in which the differential is set to the third set value P3 will be described. In this case, for the third set value P3, the third upper limit pressure P3H and the third lower limit pressure P3L are set. When the pressure rises, the compressor 5 stops when the pressure exceeds the third upper limit pressure P3H, and when the pressure drops, When it becomes less than the third lower limit pressure P3L, the compressor 5 is driven.

  Next, an example in the case of proportionally controlling the compressor 5 will be described. In this case, based on the pressure detected by the second sensor 26, the compressor 5 is proportionally controlled within the range between the third upper limit pressure P3H and the third lower limit pressure P3L and with the third upper limit pressure P3H as a set value (target value). To do. Here, at the third upper limit pressure P3H or higher, the compressor 5 stops, and at less than the third lower limit pressure P3L, the compressor 5 operates at full load. Note that PID control may be performed instead of proportional control.

  By the way, when the heat pump 2 has a plurality of stages, when the control is performed based on the detected pressure of the second sensor 26, for example, the compressor 5 of the uppermost heat pump 2 is controlled based on the detected pressure of the second sensor 26. The compressor 5 of each lower heat pump 2 may be controlled based on the pressure or temperature of the refrigerant in the condenser 6 of the corresponding heat pump 2 (or the refrigerant in the evaporator 8 of the upper heat pump 2). . Such control is the same when the control by the second sensor 26 is performed in the switching control between the second sensor 26 and the third sensor 29 described later.

<(3) Control by third sensor 29>
FIG. 6 is a schematic diagram showing a correspondence relationship between the detected pressure or detected temperature of the third sensor 29 and the operating state of the compressor 5. Here, the compressor 5 is turned on / off at the fourth set value (the fourth set pressure P4 or the fourth set temperature T4).

  In the following, a case will be described in which the third sensor 29 is a pressure sensor, the fourth set value is set as the pressure value P4, and the compressor 5 is pressure-controlled. However, the third sensor 29 is a temperature sensor. The fourth set value may be set as the temperature value T4, and the compressor 5 may be temperature controlled. In that case, if P4 is read as T4 and PH is read as TH, the same control is possible.

  If the detected pressure of the third sensor 29 is less than the fourth set value P4, the compressor 5 is stopped because the desired steam cannot be obtained even if the heat pump 2 is operated. When the detected pressure of the third sensor 29 becomes equal to or higher than the fourth set value P4, the compressor 5 is driven and steam is generated by the heat pump 2. Thereafter, if the detected pressure of the third sensor 29 further increases and exceeds the upper limit value PH, the compressor 5 may be forcibly stopped. On the other hand, when the detected pressure of the third sensor 29 becomes less than the fourth set value P4, the compressor 5 is stopped.

  Needless to say, a differential (operation gap) is set as desired in the fourth set value P4. Further, the compressor 5 may be proportionally controlled or PID controlled by adjusting the rotational speed, for example, instead of on / off control of driving and stopping thereof. This case will be described with reference to FIG. In FIG. 7, the range between the fourth upper limit pressure P4H and the fourth lower limit pressure P4L is a differential or proportional band of the fourth set value P4.

  First, the on / off control in which the differential is set to the fourth set value P4 will be described. In this case, for the fourth set value P4, the fourth upper limit pressure P4H and the fourth lower limit pressure P4L are set. When the pressure rises, the compressor 5 is driven when the pressure exceeds the fourth upper limit pressure P4H. When it becomes less than the fourth lower limit pressure P4L, the compressor 5 stops.

  Next, an example in the case of proportionally controlling the compressor 5 will be described. In this case, based on the pressure detected by the third sensor 29, the compressor 5 is proportionally controlled in the range of the fourth upper limit pressure P4H and the fourth lower limit pressure P4L and with the fourth lower limit pressure P4L as a set value (target value). To do. Here, if it is less than the fourth lower limit pressure P4L, the compressor 5 stops, and if it is equal to or higher than the fourth upper limit pressure P4H, the compressor 5 operates at full load. Note that PID control may be performed instead of proportional control.

  By the way, when the heat pump 2 has a plurality of stages, when the control is performed based on the detected pressure or detected temperature of the third sensor 29, for example, the compressor 5 of the lowermost heat pump 2 has the detected pressure or detected temperature of the third sensor 29. The compressor 5 of each upper heat pump 2 is controlled based on the pressure or temperature of the refrigerant in the evaporator 8 of the corresponding heat pump 2 (or the refrigerant in the condenser 6 of the lower heat pump 2). Control may be performed based on the above. Such control is the same when the control by the third sensor 29 is performed in the switching control between the second sensor 26 and the third sensor 29 described later.

<(4) Switching control between second sensor 26 and third sensor 29>
It can be said that the switching control between the second sensor 26 and the third sensor 29 is a combination of the control according to FIG. 5 and the control according to FIG. Specifically, first, the compressor 5 is in a range between the third upper limit pressure P3H and the third lower limit pressure P3L based on the detected pressure of the second sensor 26, and is proportional to the third upper limit pressure P3H as a set value. Controllable. Further, the compressor 5 can be proportionally controlled based on the pressure detected by the third sensor 29 within a range between the fourth upper limit pressure P4H and the fourth lower limit pressure P4L and using the fourth lower limit pressure P4L as a set value. . Then, at the set timing (for example, every set time), the first deviation rate η1 and the second deviation rate η2 are obtained by the following equations, and the deviation rate of the control by the second sensor 26 and the control by the third sensor 29 is calculated. The compressor 5 may be controlled by appropriately switching to the smaller control. Specifically, when the relationship of η1 <η2 is satisfied, the compressor 5 may be proportionally controlled based on the detected pressure of the second sensor 26. When the relationship of η1> η2 is satisfied, the detected pressure of the third sensor 29 is increased. Based on this, the compressor 5 may be proportionally controlled. In the following equation, the current pressure P is detected by the second sensor 26, and the current pressure P ′ is detected by the third sensor 29.

First deviation rate η1 = (third upper limit pressure P3H−current pressure P) / (third upper limit pressure P3H−third lower limit pressure P3L)
Second deviation rate η2 = (current pressure P′−fourth lower limit pressure P4L) / (fourth upper limit pressure P4H−fourth lower limit pressure P4L)

  The smaller the deviation rate is, the closer to the target value, the smaller the operation amount of the compressor 5. If an attempt is made to control the compressor 5 with a larger deviation rate, that is, a larger operation amount, the smaller deviation rate, that is, the smaller operation amount, will soon reach the target value. However, the frequency at which the compressor 5 stops can be reduced by appropriately switching to the control with the smaller deviation rate. Moreover, even if it stops, it can transfer to a stop state gradually. Furthermore, there is no need to manually set pressure control or temperature control.

  In the control by the third sensor 29, the case where the third sensor 29 is a pressure sensor and the fourth set value is set by the pressure value P4 (fourth upper limit pressure P4H, fourth lower limit pressure P4L) has been described. The third sensor 29 may be a temperature sensor, and the fourth set value may be set as a temperature value T4 (fourth upper limit temperature T4H, fourth lower limit temperature T4L). In that case, the current temperature T ′ may be detected by the third sensor 29, the second deviation rate η2 may be calculated using the following equation, and similarly controlled.

  Second deviation rate η2 = (current temperature T′−fourth lower limit temperature T4L) / (fourth upper limit temperature T4H−fourth lower limit temperature T4L)

  The third upper limit pressure P3H is the third upper limit value, the third lower limit pressure P3L is the third lower limit value, the fourth upper limit pressure P4H and the fourth upper limit temperature T4H are the fourth upper limit value, the fourth lower limit pressure P4L, and the fourth lower limit value. By calculating the temperature T4L as the fourth lower limit value and the detected values of the second sensor 26 and the third sensor 29 as current values, the calculation formulas for the first deviation rate η1 and the second deviation rate η2 can be summarized as follows. it can.

First deviation rate η1 = (third upper limit value−current value) / (third upper limit value−third lower limit value)
Second deviation rate η2 = (current value−fourth lower limit value) / (fourth upper limit value−fourth lower limit value)

  The control by the second sensor 26 and the control by the third sensor 29 may be switched based on the operation amount of the compressor 5 in addition to switching based on the deviation rate as described above. Also in this case, the compressor 5 performs proportional control or PID in the range between the third upper limit pressure P3H and the third lower limit pressure P3L and the third upper limit pressure P3H as a set value based on the detected pressure of the second sensor 26. Controllable. Further, the compressor 5 is based on the detected pressure (or detected temperature) of the third sensor 29, the fourth upper limit pressure P4H (or the fourth upper limit temperature T4H), the fourth lower limit pressure P4L (or the fourth lower limit temperature T4L), And the fourth lower limit pressure P4L (or the fourth lower limit temperature T4L) can be set as a set value for proportional control or PID control. Then, at the set timing (for example, every set time), the operation amount of the compressor 5 in the control by the second sensor 26 and the operation amount of the compressor 5 in the control by the third sensor 29 are obtained, and the control by the second sensor 26 is performed. And the control by the third sensor 29, the compressor 5 may be controlled with the smaller operation amount. For example, when the control by the second sensor 26 requires the operation amount X, while the control by the third sensor 29 requires the operation amount Y, if the relationship X <Y holds, the second sensor 26 The compressor 5 may be controlled based on the detected pressure, and if the relationship X> Y, the compressor 5 may be controlled based on the detected pressure (or detected temperature) of the third sensor 29.

  In the case of switching control based on the operation amount, when the heat pump 2 has a plurality of stages, the operation amount (first operation) of the uppermost compressor 5 in the control by the second sensor 26 at the set timing (for example, every set time). The value y1 / y2 of the ratio of the first operation amount y1 to the second operation amount y2 is calculated from the amount y1) and the operation amount (second operation amount y2) of the lowermost compressor 5 in the control by the third sensor 29. If this value is less than a preset constant, control by the second sensor 26 is performed, and if it is equal to or greater than the constant, control by the third sensor 29 may be performed.

  FIG. 8 is a schematic view showing Example 2 of the steam system 1 of the present invention. The steam system 1 according to the second embodiment is basically the same as the first embodiment. Therefore, in the following description, differences between the two will be mainly described, and corresponding portions will be described with the same reference numerals.

  In the first embodiment, the steam system 1 includes the heat pump 2, but in the second embodiment, a steam compressor 30 is provided instead of the heat pump 2. In the first embodiment, the ejector 4 sucks and discharges the steam from the condenser 6 of the heat pump 2. In the second embodiment, the ejector 4 sucks the steam from the steam compressor 30. Discharge.

  The steam compressor 30 is a device that sucks in, compresses and discharges steam. The vapor compressor 30 is not particularly limited in its configuration, but is, for example, a screw-type vapor compressor. A screw-type steam compressor is a device that sucks steam between screw rotors that rotate while meshing with each other, and compresses and discharges the steam by rotation of the screw rotor. However, the steam compressor 30 is not limited to a screw type as long as it compresses and discharges steam, and may be a reciprocating type or the like.

  The vapor compressor 30 includes a vapor compressor main body and a drive device for the vapor compressor, and the drive device includes an engine (typically a gas engine or a diesel engine) and / or a motor. As a specific aspect of the control of the steam compressor 30, for example, the drive device is on / off controlled. Alternatively, a power transmission device (clutch and / or transmission) from the drive device to the steam compressor body is provided between the steam compressor body and the drive device, and power is transmitted from the drive device to the steam compressor body. The power transmission device is controlled so as to change the presence / absence and amount of the power. Or the motor which comprises a drive device is controlled by an inverter, and the rotation speed of a motor is changed. Alternatively, the engine output constituting the drive device is controlled to change the engine output. The vapor compressor 30 may be controlled by combining a plurality of these. In addition, when using a motor as a drive device, you may drive a motor with the electric power of SOFC (solid oxide fuel cell).

  In the second embodiment, the steam compressor 30 sucks in steam through the supply path 27, compresses it, and discharges it. More specifically, in the illustrated example, the vapor compressor 30 is connected to a separator container 31 having a hollow container shape via a supply path 27. Then, steam (for example, flash steam, unused steam, low-pressure steam) is supplied to the separator tank 31 via the inflow path 32. The steam condensate is appropriately drained through a discharge path 33 from the separator tank 31, and the steam is supplied to the steam compressor 30 through a supply path 27. Thus, the separator tank 31 functions as a gas-liquid separator.

  In the second embodiment, the second sensor 26 is provided in the second steam path 15 from the steam compressor 30 to the suction unit 18 of the ejector 4. The third sensor 29 is provided in the separator tank 31 or the supply path 27 from the separator tank 31 to the vapor compressor 30.

  Also in the second embodiment, the steam supply valve 21 and / or the throat adjustment mechanism 22 are controlled based on the detection value of the first sensor 25. Further, the steam compressor 30 is controlled based on the detection value of one or both of the second sensor 26 and the third sensor 29. Specifically, in addition to (1) control by the first sensor 25, (2) control by the second sensor 26, (3) control by the third sensor 29, (4) the second sensor 26 and the third sensor 29, One of the switching controls is performed. Among these, the control by the first sensor 25 is the same as in the first embodiment, and the control using the second sensor 26 and the third sensor 29 and the switching control thereof are the compression of the heat pump 2 in the first embodiment. Instead of controlling the machine 5, the second embodiment is different in that the steam compressor 30 is controlled. Other configurations and controls are the same as those in the first embodiment, and thus description thereof is omitted.

  By the way, the steam compressor 30 is not limited to a single stage, and may have a plurality of stages. In that case, the lowermost stage steam compressor 30 sucks, compresses and discharges the steam from the separator tank 31, and the upper stage. Each of the steam compressors 30 sucks, compresses and discharges the steam from the one lower steam compressor 30, and the steam from the uppermost steam compressor 30 is sent to the suction unit 18 of the ejector 4. When controlling based on the detected pressure of the second sensor 26, for example, the uppermost steam compressor 30 is controlled based on the detected pressure of the second sensor 26, and the lower steam compressors 30 are controlled by Control may be based on the vapor pressure on the outlet side. Further, when controlling based on the detected pressure or detected temperature of the third sensor 29, for example, the lowermost steam compressor 30 is controlled based on the detected pressure or detected temperature of the third sensor 29, and the respective upper steams are controlled. The compressor 30 may be controlled based on the vapor pressure on the inlet side. Also in this case, instead of controlling the compressor 5 of the heat pump 2 in the first embodiment, the present embodiment 2 differs from the first embodiment only in that the steam compressor 30 is controlled, and a plurality of heat pumps 2 in the first embodiment are provided. It can be controlled in the same way as in the case of stages.

  FIG. 9 is a schematic diagram showing Example 3 of the steam system 1 of the present invention. The steam system 1 according to the third embodiment is basically the same as the first embodiment and the second embodiment. Therefore, in the following description, differences between the two will be mainly described, and corresponding portions will be described with the same reference numerals. The description of the same configuration and control as those of the first embodiment and the second embodiment is omitted.

  In the first embodiment, the steam system 1 includes the heat pump 2, and in the second embodiment, the steam system 1 includes the steam compressor 30, but in the third embodiment, both the heat pump 2 and the steam compressor 30 are provided. Is provided. Specifically, in the first embodiment, the steam compressor 30 is provided in the second steam path 15, and the steam from the condenser 6 of the heat pump 2 is boosted by the steam compressor 30 to the suction unit 18 of the ejector 4. It is the structure which discharges.

  In the third embodiment, as in the first embodiment, the first sensor 25 is provided in the third steam path 19 from the ejector 4, and the second steam path from the steam compressor 30 to the suction portion 18 of the ejector 4. 15 is provided with a second sensor 26. A third sensor 29 is provided in the supply path 27 to the evaporator 8 or the discharge path 28 from the evaporator 8 of the heat pump 2. Further, a fourth sensor 35 is provided in the fourth steam path 34 from the condenser 6 of the heat pump 2 to the steam compressor 30. The first sensor 25, the second sensor 26, and the fourth sensor 35 are pressure sensors, and the third sensor 29 is a pressure sensor or a temperature sensor. However, the fourth sensor 35 may be a sensor that detects the pressure of the refrigerant in the condenser 6 of the heat pump 2. At that time, the pressure of the refrigerant in the condenser 6 may be detected at any location from the outlet of the compressor 5 to the inlet of the expansion valve 7.

  Also in the third embodiment, the steam supply valve 21 and / or the throat adjustment mechanism 22 are controlled based on the detection value of the first sensor 25. In addition, the compressor 5 and the steam compressor 30 are controlled based on the detection value of one or both of the second sensor 26 and the third sensor 29. Specifically, in addition to (1) control by the first sensor 25, (2) control by the second sensor 26, (3) control by the third sensor 29, (4) the second sensor 26 and the third sensor 29, One of the switching controls is performed. Among these, the control by the first sensor 25 is the same as in the first embodiment, and the control using the second sensor 26 and the third sensor 29 and the switching control thereof are performed by a plurality of heat pumps 2 in the first embodiment. In the case of the stage, a steam compressor 30 is installed in place of the uppermost heat pump 2, and the steam compressor 30 may be similarly controlled instead of controlling the compressor 5 of the uppermost heat pump 2.

  That is, in the control by the second sensor 26, the steam compressor 30 is controlled based on the detected pressure of the second sensor 26, and the compressor 5 of the heat pump 2 is controlled based on the detected pressure of the fourth sensor 35. In the control by the third sensor 29, the compressor 5 of the heat pump 2 is controlled based on the detected pressure or detected temperature of the third sensor 29, and the steam compressor 30 is controlled based on the detected pressure of the fourth sensor 35. The

  In the control by the second sensor 26, as in the first embodiment, the steam compressor 30 is controlled to be turned on / off at the third set value P3, or proportional control or PID control is performed so as to maintain the third set value P3. Just do it. At this time, as described above, the compressor 5 of the heat pump 2 is controlled based on the detected pressure of the fourth sensor 35.

In the control by the third sensor 29, as in the first embodiment, the compressor 5 is proportionally controlled to be turned on / off at the fourth set value P4 (T4) or maintained at the fourth set value P4 (T4). Control or PID control may be performed. At this time, as described above, the steam compressor 30 is controlled based on the detected pressure of the fourth sensor 35.
Other configurations and controls are the same as those in the first embodiment, and thus description thereof is omitted.

  FIG. 10 is a schematic diagram showing Example 4 of the steam system 1 of the present invention. The steam system 1 according to the fourth embodiment is basically the same as the first embodiment. Therefore, in the following description, differences between the two will be mainly described, and corresponding portions will be described with the same reference numerals.

  In the fourth embodiment, the drain of the steam using facility 20 is used as the heat source of the heat pump 2. A specific configuration will be described. First, the drain of the steam using facility 20 is discharged to the separator tank 31 via the first steam trap 36. The separator tank 31 is connected to the supply path 27 to the evaporator 8 at the upper part and is connected to the discharge path 33 at the lower part.

  The separator tank 31 is provided with the evaporator 8 via the supply path 27. A second steam trap 37 is provided in the discharge path 28 from the evaporator 8. Due to such a configuration, the drain of the steam using facility 20 is discharged under a low pressure by the first steam trap 36, then passes through the evaporator 8, and is further reduced to a lower atmospheric pressure by the second steam trap 37. Discharged. In other words, the drain of the steam using facility 20 is discharged through the first steam trap 36 to become flash steam and its condensed water. After being further condensed in the evaporator 8, the drain is discharged from the second steam trap 37. Discharged. In such a configuration, the fluid that gives heat to the refrigerant in the evaporator 8 can be maintained at a temperature exceeding 100 ° C. at a pressure exceeding atmospheric pressure.

  Waste water from the second steam trap 37 is returned to the water supply tank 38 to the condenser 6 and the boiler 3. At this time, the sub heater 39 may heat the refrigerant from the expansion valve 7 to the evaporator 8 by drainage from the second steam trap 37. The sub-heater 39 is an indirect heat exchanger that exchanges heat without mixing the refrigerant from the expansion valve 7 to the evaporator 8 and the waste water from the second steam trap 37. The water in the water supply tank 38 can be supplied to the condenser 6 through the water supply pump 11, the water supply valve 12, the check valve 13, and the subcooler 9, and is also supplied through the water supply pump 40 and the check valve 41. Supply to the boiler 3 is possible.

  On the other hand, the discharge passage 33 from the separator tank 31 is provided with a discharge valve 42, and the fluid from the discharge valve 42 is returned to the water supply tank 38. In this embodiment, the discharge valve 42 is a self-reducing pressure reducing valve (primary pressure adjusting valve), but may be a valve that is opened / closed or adjusted in opening degree based on the detection value of the third sensor 29. A steam trap (not shown) may be provided in parallel with the discharge valve 42. In this case, only the liquid can be sent to the supply path 27 to the evaporator 8 by discharging only the liquid from the vapor trap.

  The fourth set pressure P4 for controlling the compressor 5 based on the detection value of the third sensor 29 is set lower than the set pressure (opening pressure) of the discharge valve 42. The discharge valve 42 is opened when the upstream pressure is equal to or higher than the set pressure, so that the heat pump 2 is protected.

  In the event of an emergency or a power failure, a normally closed electromagnetic valve 43 is provided in the supply path 27 to the evaporator 8, while the discharge path 33 from the separator tank 31 is in parallel with the discharge valve 42 in a normal manner. An open solenoid valve 44 is preferably provided. In this case, normally, the electromagnetic valve 43 in the supply passage 27 is maintained in an open state, and the electromagnetic valve 44 in the discharge passage 33 is maintained in a closed state. In an emergency or power failure, the solenoid valve 43 of the supply passage 27 is closed and the solenoid valve 44 of the discharge passage 33 is opened, so that the drain from the steam use facility 20 is discharged without going through the evaporator 8. .

  A third sensor 29 including a pressure sensor or a temperature sensor is provided on the inlet side or the outlet side of the evaporator 8 so that the pressure or temperature of the heat source fluid can be detected. In the present embodiment, the third sensor 29 is provided between the separator tank 31 and the evaporator 8. However, the third sensor 29 may be provided between the evaporator 8 and the second steam trap 37 or provided in the separator tank 31. Also good. Other configurations and controls are the same as those in the first embodiment, and thus description thereof is omitted.

  By the way, in the fourth embodiment, in the illustrated example, the second steam trap 37 is provided, and the fluid flowing in the evaporator 8 is maintained at the atmospheric pressure or higher. However, in some cases, the second steam trap 37 is omitted, You may open the front-end | tip of the discharge path 28 from the evaporator 8 to atmospheric pressure as it is. In that case, the third sensor 29 is preferably a temperature sensor that measures the temperature of the condensed water on the outlet side of the evaporator 8.

  Further, as long as the flow rate of the fluid passing through the evaporator 8 can be adjusted, the configuration is not limited to the illustrated example and can be changed as appropriate. For example, instead of the first steam trap 36, a buffer tank for storing drain and an introduction valve may be provided. The introduction valve is a self-reducing pressure reducing valve (secondary pressure regulating valve), but may be a valve that is opened / closed or adjusted in opening degree based on the detection value of the third sensor 29. The drain of the steam using facility 20 can be supplied from the buffer tank to the evaporator 8 through the supply path 27 via the introduction valve, and can be discharged from the buffer tank without going through the introduction valve or the evaporator 8. Is done. In such a configuration, the fourth set value P4 for controlling the compressor 5 based on the detection value of the third sensor 29 is set lower than the set pressure (valve closing pressure) of the introduction valve. The heat pump 2 is protected by closing the introduction valve when the downstream pressure is equal to or higher than the set pressure.

  Further, in the fourth embodiment, as an application example of the first embodiment, an example in which the waste heat of the drain of the steam using facility 20 is used as a heat source to the evaporator 8 of the heat pump 2 has been described. As an application example, the drain of the steam using facility 20 may be supplied to the separator tank 31 provided on the inlet side of the steam compressor 30, and the flash steam may be boosted by the steam compressor 30.

  The steam system 1 of the present invention is not limited to the configuration of each of the embodiments described above, and can be changed as appropriate. For example, when the heat pump 2 or the steam compressor 30 is stopped because the detection value of the third sensor 29 is low, the steam supply valve 21 may be controlled to be closed.

  In the third embodiment, the example in which the single-stage heat pump 2 and the single-stage steam compressor 30 are combined has been described. However, as described in the first and second embodiments, Both may have a plurality of stages. In that case, the heat pump 2 described in the first embodiment can be controlled in the same manner as in the case of a plurality of stages. That is, regarding the control, the vapor compressor 30 can be regarded as being equivalent to the compressor 5 of the heat pump 2.

  Moreover, in each said Example, you may plan water injection | pouring suitably in the steam compressor 30 or its inlet_port | entrance or exit. At this time, it is preferable to adjust the amount of water injection based on the rotational speed of the steam compressor 30 or based on the steam pressure on the inlet side or the outlet side of the steam compressor 30 and the rotational speed of the steam compressor 30. For example, in the said Example 2, what is necessary is just to adjust the amount of water injection to the steam compressor 30 based on the rotation speed of the steam compressor 30, and the detection value of the 2nd sensor 26 or the 3rd sensor 29 as needed.

DESCRIPTION OF SYMBOLS 1 Steam system 2 Heat pump 3 Boiler 4 Ejector 5 Compressor 6 Condenser 7 Expansion valve 8 Evaporator 14 First steam path 15 Second steam path 16 Nozzle 18 Suction part 19 Third steam path 21 Steam supply valve 22 Node part adjustment mechanism 23 Bypass path 24 Bypass valve 25 First sensor 26 Second sensor 29 Third sensor 30 Steam compressor P1 First set value P2 Second set value P3H Third upper limit pressure (third upper limit value)
P3L 3rd lower limit pressure (3rd lower limit value)
P4H Fourth upper pressure (fourth upper limit)
P4L Fourth lower limit pressure (fourth lower limit value)
T4H Fourth upper limit temperature (fourth upper limit value)
T4L fourth lower limit temperature (fourth lower limit value)

Claims (10)

A heat pump or a vapor compressor, an ejector, a first sensor and a second sensor;
In the heat pump, a compressor, a condenser, an expansion valve, and an evaporator are sequentially connected in an annular manner to circulate a refrigerant, and heat is exchanged between the refrigerant and water in the condenser to generate steam,
The steam compressor sucks in, compresses and discharges steam,
The ejector sucks the steam from the condenser or the steam compressor by ejecting steam from the boiler from the nozzle, mixes it with the steam from the nozzle, and discharges it.
The first sensor detects the pressure of steam on the outlet side of the ejector,
The second sensor detects the pressure of steam to the suction part of the ejector,
Control the steam supply to the nozzle based on the detection value of the first sensor,
The steam system, wherein the compressor or the steam compressor is controlled based on a detection value of the second sensor. Controlling a steam supply valve provided in a steam supply path to the nozzle based on a detection value of the first sensor and / or controlling a throat adjustment mechanism for changing the size of the throat of the nozzle. The steam system according to claim 1. A bypass path connecting the steam supply path to the nozzle and the exhaust steam path from the ejector;
A bypass valve provided in the bypass passage,
When the steam supply valve is provided in the steam supply path to the nozzle, the bypass path is provided so as to branch from the upstream side of the steam supply valve,
The steam supply valve or the throat adjustment mechanism is controlled to maintain the detection value of the first sensor at a first set value,
The bypass valve has its opening / closing or opening adjusted so as to maintain the downstream pressure at the second set value,
The steam system according to claim 2, wherein the second set value is set lower than the first set value. Including both the heat pump and the vapor compressor;
The steam compressor sucks, compresses and discharges steam from the condenser,
The ejector sucks steam from the steam compressor by ejecting steam from the boiler from the nozzle, mixes it with steam from the nozzle, and discharges it.
Controlling the steam compressor based on the detection value of the second sensor;
The steam according to any one of claims 1 to 3, wherein the compressor is controlled based on a pressure of a refrigerant in the condenser or a pressure of steam sent from the condenser to the steam compressor. system. In place of or in addition to the second sensor, a third sensor is provided,
This third sensor detects the pressure or temperature of the fluid passed through or passed through the evaporator, or detects the pressure or temperature of the fluid at the inlet side of the vapor compressor,
The steam system according to any one of claims 1 to 3, wherein the compressor or the steam compressor is controlled based on a detection value of the third sensor. Including both the heat pump and the vapor compressor;
The steam compressor sucks, compresses and discharges steam from the condenser,
The ejector sucks steam from the steam compressor by ejecting steam from the boiler from the nozzle, mixes it with steam from the nozzle, and discharges it.
Controlling the compressor based on the detection value of the third sensor;
The steam system according to claim 5, wherein the steam compressor is controlled based on a pressure of a refrigerant in the condenser or a pressure of steam sent from the condenser to the steam compressor. Based on the detection value of the second sensor, the compressor or the steam compressor is proportionally controlled or PID controlled within the range between the third upper limit value and the third lower limit value, and using the third upper limit value as a set value. Or
Based on the detection value of the third sensor, the compressor or the steam compressor is proportionally controlled or PID controlled within a range between a fourth upper limit value and a fourth lower limit value, and the fourth lower limit value as a set value. ,
Based on the current value of each sensor at the set timing, the first deviation rate and the second deviation rate are obtained by the following equations, and the smaller deviation rate of the control by the second sensor and the control by the third sensor It controls by these. The steam system of Claim 5 characterized by the above-mentioned.
First deviation rate = (third upper limit value−current value) / (third upper limit value−third lower limit value)
Second deviation rate = (current value−fourth lower limit value) / (fourth upper limit value−fourth lower limit value) Based on the detection value of the second sensor, the compressor or the steam compressor is proportionally controlled or PID controlled within the range between the third upper limit value and the third lower limit value, and using the third upper limit value as a set value. Or
Based on the detection value of the third sensor, the compressor or the steam compressor is proportionally controlled or PID controlled within a range between a fourth upper limit value and a fourth lower limit value, and the fourth lower limit value as a set value. ,
The operation amount of the compressor or the steam compressor in the control by the second sensor and the operation amount of the compressor or the steam compressor in the control by the third sensor based on the current values by the sensors at the set timing The steam system according to claim 5, wherein the control is performed with a smaller operation amount of the control by the second sensor and the control by the third sensor. Including both the heat pump and the vapor compressor;
The steam compressor sucks, compresses and discharges steam from the condenser,
The ejector sucks steam from the steam compressor by ejecting steam from the boiler from the nozzle, mixes it with steam from the nozzle, and discharges it.
A fourth sensor for detecting the pressure of the refrigerant in the condenser or the pressure of the vapor sent from the condenser to the vapor compressor;
Based on the detection value of the second sensor, in the range between the third upper limit value and the third lower limit value, and the third upper limit value as a set value, the steam compressor is proportionally controlled or PID controlled,
Based on the detection value of the third sensor, in the range between the fourth upper limit value and the fourth lower limit value, and the fourth lower limit value as a set value, the compressor is proportionally controlled or PID controlled,
When controlling the steam compressor based on the detection value of the second sensor, to control the compressor based on the detection value of the fourth sensor,
When controlling the compressor based on the detection value of the third sensor, to control the steam compressor based on the detection value of the fourth sensor,
Based on the current value of each sensor at the set timing, the first deviation rate and the second deviation rate are obtained by the following equations, and the smaller deviation rate of the control by the second sensor and the control by the third sensor It controls by these. The steam system of Claim 5 characterized by the above-mentioned.
First deviation rate = (third upper limit value−current value) / (third upper limit value−third lower limit value)
Second deviation rate = (current value−fourth lower limit value) / (fourth upper limit value−fourth lower limit value) Including both the heat pump and the vapor compressor;
The steam compressor sucks, compresses and discharges steam from the condenser,
The ejector sucks steam from the steam compressor by ejecting steam from the boiler from the nozzle, mixes it with steam from the nozzle, and discharges it.
A fourth sensor for detecting the pressure of the refrigerant in the condenser or the pressure of the vapor sent from the condenser to the vapor compressor;
Based on the detection value of the second sensor, in the range between the third upper limit value and the third lower limit value, and the third upper limit value as a set value, the steam compressor is proportionally controlled or PID controlled,
Based on the detection value of the third sensor, in the range between the fourth upper limit value and the fourth lower limit value, and the fourth lower limit value as a set value, the compressor is proportionally controlled or PID controlled,
When controlling the steam compressor based on the detection value of the second sensor, to control the compressor based on the detection value of the fourth sensor,
When controlling the compressor based on the detection value of the third sensor, to control the steam compressor based on the detection value of the fourth sensor,
From the first operation amount (y1) of the steam compressor in the control by the second sensor and the second operation amount (y2) of the compressor in the control by the third sensor at the set timing, the first operation A ratio value (y1 / y2) of the amount (y1) to the second manipulated variable (y2) is obtained, and if this value is less than a preset constant, control is performed by the second sensor, while if it is greater than or equal to the constant The steam system according to claim 5, wherein control is performed by the third sensor.

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