JP2015024357A - Method for operating heat pump type concentration apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To develop a method for operating a new heat pump type concentration apparatus that can realize a curtailment of start-up time and a stabilization of the start-up although a waste of auxiliary vapor and that of an excessive design are eliminated by preventing auxiliary vapor particularly upon a rise from being discharged carelessly from a heating can.SOLUTION: A control to adjust so that an opening degree of an exhaust valve V15 provided between a drain port 15 in a heating can 1 and a vacuum pump 5 may decrease with an elapse of time is started at the point of time when a pressure in an evaporator 2 decreases down to a desired value. Further, an operation control of a compressor 7 is started at this point of time. Thereafter, when an operation frequency of the compressor 7 increases up to a desired value, the control to adjust an opening degree of the exhaust valve V15 is changed to a control based on a drain temperature of the heating can 1, and a control of an opening degree of an auxiliary vapor supply valve V14 is started.

Description

  The present invention relates to an apparatus used for concentrating various seasonings, various extracts, factory waste liquids, and the like, and particularly relates to an operation method of a heat pump type concentrator provided with a heating can and an evaporation can. .

Traditionally, various liquid substances such as herbal medicine extracts, various seasonings, animal extracts, seafood extracts, plant extracts, fermentation liquids, aqueous solutions such as amino acids, yeasts, proteins, and various waste liquids are used as liquid raw materials. As an example of an apparatus for concentrating, a heat pump type concentrating apparatus is used (see, for example, Patent Document 1).
As shown in FIG. 1, such a heat pump type concentrator C forms a circulation path by connecting a heating can 1 and an evaporator 2 by a blow pipe 3 and a return pipe 4, and a vacuum pump 5. The atmosphere in the circulation path is extracted by the above, the inside of the circulation path is evacuated, supplied to the evaporator 2, and then the liquid that has flowed into the long pipe 11 disposed in the heating can 1 through the return pipe 4. The solvent component is evaporated by boiling from the steam supplied to the outside of the long pipe 11, and the liquid component L1 and the vapor component S0 having increased concentrations are blown into the evaporator 2, and the evaporator 2 The apparatus is configured to separate the liquid component L1 and the vapor component S0 in the inside to obtain a high-concentration liquid.
In addition, when starting up the heat pump type concentrator C, the auxiliary steam SS generated by the steam supply device 9 is used as the steam supplied to the outside of the long pipe 11.
Then, the steam component S0 discharged from the evaporator 2 is heated by the compressor 7 to be heated steam S1, and this heated steam S1 is supplied into the heating can 1 (outside the long tube 11) and auxiliary steam. The supply amount of SS is reduced to shift to steady operation.

In the operation of such a heat pump type concentrator C, conventionally, an operation according to the flowchart shown in FIG. 7 is performed as an example, and a plurality of controls (four types of controls shown below as an example) are performed in parallel. It has been broken.
First, as a first control, the pressure (substantially temperature) in the evaporator 2 is measured, and the rotation speed (inverter frequency) of the compressor 7 is controlled according to this value (in FIG. 7). # 6).
Further, as a second control, the drain temperature of the heating can 1 is measured, and a drain port in the heating pump 1 is provided on the inlet side of the vacuum pump 5 for reducing the pressure in the heat pump type concentrator C (the drain port in the heating can 1). 15 and the opening (gas exhaust amount) of the exhaust valve V15 (provided between the vacuum pump 5) is controlled (# 8 in FIG. 7).
As a third control, the pressure (substantially temperature) in the heating can 1 is measured, and the opening degree of the flow rate adjusting valve V14 (auxiliary steam supply) for adjusting the supply amount of auxiliary steam according to this value. Amount) is controlled (# 9 in FIG. 7).
As a fourth control, the amount of liquid in the evaporator 2 is measured, and the opening degree of the valve V8 for adjusting the amount of liquid raw material supplied to the nozzle 82 is controlled (in FIG. 7). # 4).

And by performing such four types of control in parallel, the pressure in the heating can 1, the pressure in the evaporator 2, and the frequency of the compressor 7 in the heat pump type concentrator C are shown by the solid line in FIG. 4. In this example, it took about 200 minutes to increase to a value at which steady operation is possible.
Such a heat pump type concentrator C is generally operated continuously for 24 hours, and once started up, it will not be stopped for a long time. The fact is that it was not so important.
Further, the time required for starting up the heat pump type concentrator C depends on the supply speed of the auxiliary steam SS, and if the supply speed is high, the temperature in the heating can 1 is likely to rise, and the start-up time is shortened. Can do. However, it is not realistic from the viewpoint of cost and control to secure a large supply capacity compared to the auxiliary steam supply amount in the steady state.
Therefore, the present applicant examined the operation at the time of starting up the heat pump type concentrator C, and when the temperature of the drain D of the heating can 1 is considerably lower than the set value (SP value) in the second control, It is mistaken that there is a lot of inert gas, the operation control for fully opening the exhaust valve V15 continues for a long time, and the auxiliary steam SS is exhausted excessively from the heating can 1, resulting in heating. It was found that the rise in pressure in the can 1 was hindered and the time until steady operation was increased.

JP 2005-111319 A

  The present invention has been made in view of such a background, in particular, by preventing the auxiliary steam at the start-up from being inadvertently discharged from the heating can, to eliminate the waste of auxiliary steam, The technical challenge is to develop a new heat pump type concentrator operation method that can reduce the startup time and stabilize the startup while eliminating excessive design.

  That is, according to the operation method of the heat pump type concentrator according to claim 1, the circulation path is formed by connecting the heating can and the evaporation can by the blow pipe and the return pipe, and the atmosphere in the circulation path by the vacuum pump. From the vapor supplied to the outside of the long pipe, the liquid flowing into the long pipe arranged in the heating can through the return pipe after the inside of the circulation path is evacuated and supplied into the evaporator The solvent component is evaporated by boiling by heating, and the liquid component and the vapor component having increased concentrations are blown into the evaporator, and the liquid component and the vapor component are separated in the evaporator to obtain a high concentration. An apparatus for obtaining a liquid, wherein the vapor component discharged from the evaporator is heated by a compressor to form a vapor, and the heat pump type thickener is configured to supply the vapor into the heating can. In the operation of the apparatus, when starting up the heat pump type concentrator, the vacuum pump is started and auxiliary steam is supplied into the heating can without starting the compressor. When the pressure drops to the desired value, control is started so that the opening of the valve provided between the drain port of the heating can and the vacuum pump decreases with the passage of time. Then, when the operation frequency of the compressor rises to a predetermined value, control for adjusting the opening of the exhaust valve is performed on the drain temperature of the heating can. The control is changed to the control based on the above, and the opening degree control of the auxiliary steam supply valve is started.

  The operation method of the heat pump type concentrator according to claim 2 is that the circulation path is formed by connecting the heating can and the evaporation can by the blow pipe and the return pipe, and the atmosphere in the circulation path by the vacuum pump. From the vapor supplied to the outside of the long pipe, the liquid flowing into the long pipe arranged in the heating can through the return pipe after the inside of the circulation path is evacuated and supplied into the evaporator The solvent component is evaporated by boiling by heating, and the liquid component and the vapor component having increased concentrations are blown into the evaporator, and the liquid component and the vapor component are separated in the evaporator to obtain a high concentration. A device for obtaining a liquid, wherein the vapor component discharged from the evaporator is heated by a compressor to form a vapor, and the heat pump type concentrator configured to supply the vapor into the heating can In this operation, when starting up the heat pump type concentrator, the vacuum pump is started without starting the compressor, and auxiliary steam is supplied into the heating can. When the pressure drops to the desired value, control is started to adjust the opening degree of the exhaust valve provided between the drain port of the heating can and the vacuum pump based on the pressure in the heating can. Then, when the operation frequency of the compressor rises to a predetermined value, control for adjusting the opening of the exhaust valve is performed on the drain temperature of the heating can. The control is changed to the control based on the above, and the opening degree control of the auxiliary steam supply valve is started.

Furthermore, the operation method of the heat pump type concentrator according to claim 3 is characterized in that, in addition to the requirements, a minimum operation amount of the exhaust valve is set.
The above problems can be solved by using the configuration of the invention described in each of the claims as a means.

  First, according to the first aspect of the present invention, it is possible to eliminate the waste of steam by preventing accidental discharge of auxiliary steam from the heating can, and to supply auxiliary steam to a plurality of systems. It is possible to realize a reduction in start-up time and stabilization of start-up while eliminating excessive design such as. As a result, the running cost can be reduced.

  According to the invention described in claim 2, particularly, the auxiliary steam is prevented from being inadvertently discharged from the heating can, thereby eliminating waste of steam and supplying the auxiliary steam to a plurality of systems. It is possible to realize a reduction in start-up time and stabilization of start-up while eliminating excessive design such as. As a result, the running cost can be reduced.

  Furthermore, according to the invention described in claim 3, it is possible to prevent an inert gas exhaust failure during steady operation and to measure an accurate pressure.

It is a side view which shows the whole heat pump type concentration apparatus which is an application object of this invention skeleton. It is a flowchart which shows the flow of the operating method of the heat pump type concentration apparatus of this invention. It is a timeline which shows the state of the heat pump type concentration apparatus when the starting operation is performed by this invention. It is a graph for comparing the operating method of the heat pump type concentrator of the present invention and the pressure of the evaporator, the pressure of the heating can, and the frequency of the inverter driving the compressor by the operating method of the conventional heat pump type concentrator. It is a timeline which shows the state of the heat pump type | formula concentrator when the starting operation is performed by the other Example of this invention. It is a timeline which shows the state of the heat pump type | formula concentrator when the starting operation is performed by the conventional method. It is a flowchart which shows the flow of the operating method of the conventional heat pump type concentrator.

  Hereinafter, the operation method of the heat pump type concentrator of the present invention will be described. First, the configuration of the heat pump type concentrator will be described with reference to the drawings, and then the heat pump of the present invention will be described together with the operation mode of the apparatus. An operation method of the type concentrator will be described.

What is indicated by a symbol C in the figure is a heat pump type concentrator to which the present invention is applied. This device is connected between the heating can 1 and the evaporator 2 by a blow-in conduit 3 and a return conduit 4 and circulates. A path is formed. Then, the liquid raw material L0 is caused to flow into the long tube 11 disposed in the heating can 1, and the liquid raw material L0 is boiled by the conduction heat from the heating medium supplied to the outside of the long tube 11, thereby causing the solvent component to boil. The liquid component L1 and the vapor component S0 in a state where the concentration is increased are blown into the evaporator 2 and the liquid component L1 and the vapor component S0 are separated in the evaporator 2. .
As the heating medium supplied to the outside of the long pipe 11, the auxiliary steam SS is used at the time of startup, and the steam component S0 separated mainly in the evaporator 2 is heated by the compressor 7 during steady operation. Steam S1 is used.

Hereinafter, various members constituting the heat pump type concentrator C will be described in detail.
First, the heating can 1 will be described. In this case, a plurality of long pipes 11 which are pipes made of a heat-resistant material such as metal are provided in a casing 10 in which confidentiality is ensured. 11 is in communication with the liquid supply port 12 formed in the lower portion of the housing 10, while the upper end of the long tube 11 is in communication with the discharge port 13 formed in the upper portion of the housing 10.
Further, a steam port 14 and a drain port 15 are formed in a side peripheral portion of the housing 10. Note that the fluid flowing from both the liquid supply port 12 through the long pipe 11 to the discharge port 13 and the flow channel from the vapor port 14 to the drain port 15 do not interfere with each other. In this way, only the thermal energy moves between the two flow paths.
Furthermore, a steam supply device 9 is connected to the steam port 14 formed in the heating can 1 by a pipe line, and this pipe line is provided with a flow rate adjusting valve V14.

Next, the evaporator 2 will be described. In this example, an exhaust port 21 is formed in the upper portion of the casing 20 which is a hollow member in which an inverted conical portion is connected to the lower portion of the cylindrical portion, and an inflow port is formed in the side peripheral portion. 22 is formed, and a discharge port 23 is formed in the lower part. A liquid level sensor 25 is provided at the lower part of the housing 20.
Furthermore, a nozzle 82 is disposed in the housing 20, and the liquid raw material L 0 stored in the liquid supply tank 8 is ejected from the nozzle 82. The amount of the liquid material L0 ejected by the nozzle 82 is adjusted by adjusting the opening of a valve V8 provided between the liquid supply tank 8 and the nozzle 82.

The discharge port 13 in the heating can 1 and the inflow port 22 in the evaporator 2 are connected to each other by a blow-in conduit 3, and the liquid supply port 12 in the heating can 1 and the discharge in the evaporator 2 are connected. The outlet 23 is connected in a communicating state by a return pipe 4. As a result, a circulation path including the evaporator 2, the return pipe 4, the long pipe 11, and the blowing pipe 3 is formed.
The return conduit 4 is formed with a concentrate discharge port 41, and is configured so that the concentrated liquid component L1 can be discharged to the outside by opening the valve.
The drain port 15 of the heating can 1 is connected to a pipe line including a drain tank 16, a valve V16, and a vacuum pump 5, and further includes an exhaust valve V15 in parallel with the drain tank 16 and the valve V16. The pipe line is provided in a bypass shape.

  Further, a compressor 7 is provided between the exhaust port 21 in the evaporator 2 and the steam port 14 in the heating can 1. The compressor 7 is driven by an inverter motor M as an example. A Roots blower with a discharge pressure of about 0.2 MPaG is applied. In this embodiment, a roots blower having a three-leaf type rotor 71 is employed, but a two-leaf type one can also be applied. The casing of the compressor 7 is appropriately cooled by cooling water.

  Further, the exhaust port 21 and the compressor 7 in the evaporator 2 are connected by a pipe 72, and a demister 76 is provided between the compressor 7 and the evaporator 2 in the pipe 72. .

  Although not shown, the liquid raw material L0 may be supplied into the evaporator 2 after being heated by the preheater. In this case, in the preheater, the uncondensed product discharged from the heating can 1 is supplied. It is preferable to adopt a form in which heat exchange is performed between the gas S2 and the drain D and the liquid raw material L0.

The pressure sensor P1 is provided to position the sensing unit in the housing 10 of the heating can 1, and the pressure sensor P2 is provided to position the sensing unit in the housing 20 of the evaporation can 2. It is done. Further, a temperature sensor T for measuring the temperature of the drain D is provided in a pipe line connecting the drain port 15 and the drain tank 16.
Further, the drain tank 16 is provided with a liquid level sensor 17 for detecting the height of the liquid level of the drain D.
These pressure sensor P1, pressure sensor P2, temperature sensor T, liquid level sensor 17 and liquid level sensor 25 are connected to an appropriate control device (not shown).

  The heat pump type concentrator C to which the present invention is applied is configured as described above as an example. Hereinafter, the operation method of the heat pump type concentrator C of the present invention will be described with reference to the flowchart shown in FIG. A description will be given along the timeline shown in FIG.

〔Start-up〕
First, the opening of the exhaust valve V15 is maximized (# 1), and then the operation of the vacuum pump 5 is started (# 2) to reduce the pressure in the circulation system in the heat pump type concentrator C. The evaporator 2, the pipe line connecting these, and the inside of the device are depressurized. At this time, the compressor 7 is not started.
In such a state, the opening degree of the valve V8 is adjusted, and various liquid substances such as herbal medicine extracts, various seasonings, animal extracts, seafood extracts, plant extracts, fermentation liquids, and aqueous solutions of amino acids, yeasts, proteins, etc. Or various waste liquids etc. are thrown into the evaporator 2 as the liquid raw material L0. At this time, since the inside of the evaporator 2 is under reduced pressure and is lower than the atmospheric pressure, the liquid raw material L0 is sucked (introduced) into the evaporator 2 simply by opening the valve V8. In addition, instead of suction using low pressure in this way, the liquid raw material L0 may be input using a pump as appropriate.
Thereafter, the amount of liquid in the evaporator 2 is measured by the liquid level sensor 25, and the amount of the liquid raw material L0 supplied to the nozzle 82 is adjusted by controlling the opening degree of the valve V8 (# 3). ).
Next, the auxiliary steam SS is supplied to the heating can 1 (# 4), and the flow rate of the auxiliary steam SS is maximized by controlling the opening of the flow rate adjusting valve V14 to the maximum. The
The measured value of the pressure sensor P1, the measured value of the pressure sensor P2, the measured value of the temperature sensor T, and the measured value of the liquid level sensor 17 are monitored by an appropriate control device.
In addition, since the opening degree of the exhaust valve V15 is maximized, the exhaust gas of the inert gas at the time of start-up can be prevented and an accurate pressure can be measured.

[Trigger point t1]
Eventually, when it was confirmed that the pressure in the evaporator 2 that had been reduced by the operation of the vacuum pump 5 was reduced to a predetermined value (20 kPa as an example in this embodiment) ((# 5), t1 = 50 min), the opening degree of the exhaust valve V15 is changed (# 6). Specifically, during the period from the trigger point t1 to a trigger point t2, which will be described later, control is applied such that the opening degree of the exhaust valve V15 decreases to a preset opening degree as time elapses. . Specifically, for example, the relationship between the elapsed time and the opening degree of the exhaust valve V15 is set in advance in a programmable logic controller (hereinafter abbreviated as “PLC”) provided in a control device (not shown) and set in this PLC. The opening degree of the exhaust valve V15 is controlled by time, and this change is schematically shown in FIG.
FIG. 3 shows an embodiment in which the opening degree of the exhaust valve V15 decreases linearly with the passage of time. However, as shown in FIG. 5, the opening degree of the exhaust valve V15 gradually increases with the passage of time. It is also possible to perform control that decreases gradually.

At this time (t1 = 50 min), the operation control of the compressor 7 is started (# 7). Based on the measured value of the pressure sensor P2 (pressure in the evaporator 2), the compressor 7 is controlled. The operation frequency control is started.
Specifically, while the pressure setting value is gradually changed so that the inside of the evaporator 2 becomes a target pressure set in advance, the rotation speed of the inverter motor M is set to the maximum rotation speed set in advance. At the same time, the control is performed in combination with the control for increasing / decreasing the rotational speed in accordance with the amount of increase / decrease in the rotational speed per time set in advance.
Control for increasing or decreasing the rotational speed of the inverter motor M is performed in accordance with the set value of the pressure in the evaporator 2 and the actual pressure in the evaporator 2.
Since the inverter motor M is driven in proportion to the operating frequency of the inverter, the rotation speed of the inverter motor M shows a change in the compressor frequency in FIG. 4 to be described later. This means a change in the rotational speed of the motor M.

[Trigger point t2]
By the control as described above, the pressure in the evaporator 2 increases, the operating frequency of the compressor 7 increases, and the supply amount of the auxiliary steam SS decreases accordingly.
Eventually, when the operating frequency of the compressor 7 rises to a predetermined value (t2 = 160 min) (# 8), control of the opening degree of the exhaust valve V15 based on the measured value of the temperature sensor T is started (#). 9). Specifically, when the temperature of the drain D is lower than a preset temperature applied at the time t2, the opening of the exhaust valve V15 is increased, and conversely, the opening is higher. PID control is performed to reduce the.

  At this time (t2 = 160 min), control of the opening degree of the flow rate adjustment valve V14 based on the measured value of the pressure sensor P1 is started (# 10), specifically, the pressure of the heating can 1 However, PID control is performed to increase the opening degree of the flow rate adjustment valve V14 when the pressure is lower than the preset pressure, and to reduce the opening degree of the flow rate adjustment valve V14 when the pressure is higher.

By performing the operation as described above, the liquid raw material L0 supplied into the evaporator 2 from the nozzle 82 is supplied into the long pipe 11 in the heating can 1 via the return pipe 4 and heated with steam. The liquid component L1 is pulled up when the generated vapor component S0 rises in the long tube 11 by boiling in the long tube 11. The vapor component S0 and the liquid component L1 ascend in the long pipe 11 to reach the discharge port 13 and enter the blow-in pipe 3 from there, and then flow into the housing 20 from the inlet 22 in the evaporator 2. .
The vapor component S0 and the liquid component L1 are separated in the housing 20, and the vapor component S0 reaches the compressor 7 from the exhaust port 21, where the temperature is raised, and the vapor port 14 in the heating can 1 is heated. To be supplied. At this time, mist, dust and the like contained in the vapor component S0 are removed by the demister 76.

On the other hand, the liquid component L1 accumulates in the lower part of the housing 20 and is supplied from here through the return pipe 4 to the liquid supply port 12 in the heating can 1.
By continuing such operation, the concentrated liquid component L1 is again located in the long tube 11 in the heating can 1 with the new liquid raw material L0 supplied from the nozzle 82, and further concentrated. Is done.

  Then, the above operation is continued, and when the liquid component L1 reaches a desired concentration, the valve 42 is opened and the concentrated liquid component L1 is discharged to the outside.

Further, when the liquid raw material L0 is continuously concentrated, inert gas is generated in the heating can 1 and the evaporator 2, and such inert gas is discharged to the outside by the vacuum pump 5 via the exhaust valve V15. The adverse effect of inert gas can be eliminated.
The minimum operation amount of the exhaust valve V15 is set so that the inert gas generated in the evaporator 2 and the heating can 1 can be extracted. Specifically, since the inert gas is inevitably generated, the exhaust gas is exhausted. A lower limit value (for example, 20%) of the opening is set in advance so that the minimum opening is always secured so that the valve V15 is not completely closed.
During the above operation, the drain D is accumulated in the drain tank 16, the valve V16 is opened / closed according to the liquid amount of the drain D detected by the liquid level sensor 17, and the drain D is opened to the vacuum pump 5 when the valve V16 is opened. Is sucked out and discharged to the outside.

[Comparison between the driving method of the present invention and the conventional driving method]
Here, the operation of the heat pump type concentrator C according to the conventional control method described in the background of the invention is compared with the operation of the heat pump type concentrator C according to the control method of the present invention.
The operation method of the heat pump type concentrator C according to the conventional control method is performed in accordance with the flowchart shown in FIG. 7, and the state shown in the timeline shown in FIG. 6 is obtained. Specifically, the present invention shown in FIG. The flowchart showing the conventional control method is the one that excludes the step # 6 “V15 control start” in the flowchart showing the control method.
On the other hand, the state of the heat pump type concentrator C is greatly different due to such a slight difference in the control method. As shown in FIG. 4, in the case of the conventional method, the operating frequency of the compressor 7 is It can be seen that the time required to increase to a predetermined value (t3 = 200 min) is delayed by 40 minutes compared with the case according to the present invention (t2 = 160 min).
Further, in FIG. 4, when the graph according to the present invention is compared with the graph according to the conventional method, it can be seen that the vertical fluctuation of the graph according to the conventional method is intense. This is because in the conventional method, the pressure in the evaporator 2 and the rotation speed of the compressor 7 are controlled, the opening degree of the exhaust valve V15 is controlled by the drain temperature from the heating can 1, and the pressure and flow rate in the heating can 1 are adjusted. Although the opening degree of the valve V14 is controlled independently, it is considered that these are caused by the mutual influences through the pressure and temperature in the system. In addition, since there is a large amount of air in the system at startup and the temperature of the system is low, control by such a conventional method has a time difference between the system change and mutual influence, and the corresponding control. Appearing with an error is considered to be the cause of the up and down fluctuation of the graph.

Focusing on the flow rate of the auxiliary steam SS, the flow rate from t0 to t3 in the case of the conventional method is 200% or more of the flow rate from t0 to t3 in the case of the present invention.
For this reason, the operation method of the present invention can reduce the time required for starting up the heat pump type concentrator C by preventing waste of the auxiliary steam SS. It turns out that an operation rate can be improved rather than the case where the operating method of the type | formula concentration apparatus C is used.
Further, it is not necessary to secure an excessive supply capacity of the auxiliary steam SS, and an increase in initial cost can be avoided.

[Other Examples]
Next, an embodiment of the operation method defined in claim 2 will be described.
The operation method of the heat pump type concentrator C shown in this embodiment is an exhaust valve V15 provided between the drain port 15 and the vacuum pump 5 in the heating can 1 performed between the trigger point t1 and the trigger point t2. The control for adjusting the opening degree is performed based on the pressure in the heating can 1.
Specifically, for example, in the PLC, a numerical relationship between the pressure in the heating can 1 and the opening setting value of the exhaust valve V15 is set in advance, and this numerical relationship is used during operation. The opening of the exhaust valve V15 is controlled by a signal from the PLC so that the opening corresponds to the pressure in the heating can 1 detected by the actual pressure sensor P1.
In this case, the pressure in the evaporator 2, the flow rate of the auxiliary steam SS, and the frequency of the compressor 7 also show the same changes as those in the timeline of the embodiment shown in FIG. 3.

C Heat pump type concentrator 1 Heating can 10 Housing 11 Long pipe 12 Supply port 13 Discharge port 14 Steam port 15 Drain port 16 Drain tank 17 Liquid level sensor 2 Evaporator 20 Housing 21 Exhaust port 22 Inlet port 23 Discharge port 25 Liquid level sensor 3 Blowing line 4 Return line 41 Concentrated liquid discharge port 42 Valve 5 Vacuum pump 7 Compressor 71 Rotor 72 Line 76 Demister 8 Liquid supply tank 82 Nozzle 9 Steam supply device D Drain L0 Liquid raw material L1 Liquid component M Inverter motor P1 Pressure sensor P2 Pressure sensor S0 Steam component S1 Heated steam S2 Uncondensed gas SS Auxiliary steam T Temperature sensor V16 Valve V8 Valve V14 Flow control valve V15 Exhaust valve

Claims (3)

A circulation path is formed by connecting the heating can and the evaporator with a blow-in pipe and a return pipe, and the atmosphere in the circulation path is extracted by a vacuum pump to make the inside of the circulation path into a vacuum state. Then, the liquid flowing into the long pipe disposed in the heating can through the return pipe is boiled by heating from the vapor supplied to the outside of the long pipe to evaporate the solvent component, An apparatus for obtaining a high-concentration liquid by blowing the increased liquid component and vapor component into the evaporator and separating the liquid component and vapor component in the evaporator, and discharged from the evaporator In the operation of the heat pump type concentrator configured to raise the vapor component by the compressor into the vapor and supply this vapor into the heating can, the heat pump type concentrator is started up. At the beginning, the vacuum pump is started without starting the compressor, and auxiliary steam is supplied into the heating can. When the pressure in the evaporator drops to a desired value, the heating can Starts the control to adjust the opening of the valve provided between the drain port and the vacuum pump so that it decreases with the passage of time, and further starts the operation control of the compressor at this point. Then, when the operating frequency of the compressor rises to a predetermined value, the control for adjusting the opening degree of the exhaust valve is changed to control based on the drain temperature of the heating can, and the auxiliary steam supply valve A method for operating a heat pump type concentrator, characterized in that opening degree control is started.
A circulation path is formed by connecting the heating can and the evaporator with a blow-in pipe and a return pipe, and the atmosphere in the circulation path is extracted by a vacuum pump to make the inside of the circulation path into a vacuum state. Then, the liquid flowing into the long pipe disposed in the heating can through the return pipe is boiled by heating from the vapor supplied to the outside of the long pipe to evaporate the solvent component, An apparatus for obtaining a high-concentration liquid by blowing the increased liquid component and vapor component into the evaporator and separating the liquid component and vapor component in the evaporator, and discharged from the evaporator In the operation of the heat pump type concentrator configured to raise the vapor component by the compressor into the vapor and supply this vapor into the heating can, the heat pump type concentrator is started up. At the beginning, the vacuum pump is started without starting the compressor, and auxiliary steam is supplied into the heating can. When the pressure in the evaporator drops to a desired value, the heating can Starts control to adjust the opening of the exhaust valve provided between the drain port and the vacuum pump based on the pressure in the heating can, and at this time, starts operation control of the compressor. Then, when the operating frequency of the compressor rises to a predetermined value, the control for adjusting the opening degree of the exhaust valve is changed to control based on the drain temperature of the heating can, and the auxiliary steam supply valve The operation method of the heat pump type concentrator characterized by starting the opening degree control of.
  The operation method of the heat pump type concentrator according to claim 1 or 2, wherein a minimum operation amount of the exhaust valve is set.

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