JP2008149210A - Vapor condenser in vacuum device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide the vapor condenser in a vacuum drying device capable of achieving the enhancement of a heat transfer capacity, the reduction of the transmission temperature difference loss of a cooling medium and the vacuum vapor of a condensing surface and an increase in the coefficient of the nucleate boiling heat transmission of a cooling evaporation round pipe and the coefficient of boundary film heat transmission of a circulating heating medium at the same time to develop a good heat transfer capacity and a highly efficient vapor condensing capacity. <P>SOLUTION: The cooling medium evaporation round pipe of the vapor condenser of a vacuum dryer is altered to an inner surface grooved round pipe from a smooth pipe to be subjected to deformation processing to be formed into a flat oval pipe. One or both of a pair of flat surfaces are brought to the close contact state with the inner wall surface of the passage of a heating medium liquid to be mounted into the passage, the close contact area of the cooling medium evaporation oval pipe with the inner wall surface of the heating medium liquid passage in a vapor condensing plate is increased, rods for forming turbulent flows at an equal interval are attached along the cooling medium evaporation oval pipe mounted in the liquid passage to disturb the laminar flow on the outer surface of the cooling medium evaporation oval pipe to accelerate the convection boundary film heat transfer of the heating medium liquid. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to an improvement in a steam condensing device in a vacuum apparatus, particularly a steam condensing device in a vacuum apparatus proposed as Japanese Patent No. 1177616 and Japanese Patent No. 3644845 previously developed by the present applicant.

  The vapor condensing unit (trap) of the vacuum apparatus condenses and collects the vapor of water or other solvent vaporized from the object in the vacuum chamber on a low-temperature cooling surface, and thereby adjusts the vacuum pressure of the vacuum chamber to a desired value. For the purpose of maintaining the value, the vacuum freezing device, the vacuum drying device, the vacuum concentrator, the vacuum distiller, the vacuum cooler, the desolvation device, etc. are incorporated into the vacuum device so as to constitute the main part thereof, Widely used.

  The trap (steam condensing unit) in this vacuum device is supplied with the amount of cold that condenses the vacuum steam from the low-temperature refrigerant of the refrigeration unit. From the viewpoint of heat transfer engineering, the low-temperature medium (refrigerant) and the high-temperature medium (vacuum vapor) And a heat exchanger. In a heat exchange type heat exchanger, a high temperature fluid and a low temperature fluid are partitioned by a heat transfer wall, and heat exchange is performed by passing heat. This type includes the first type of direct type (direct heat exchange of high and low temperature fluids) and the type of indirect type (indirect heat exchange through the circulation of intermediate fluid between high and low temperature fluids). There are three means: two means and a third means of triple (heat exchange between three media).

  These first to third types of vapor condensing units are explained with a schematic explanatory diagram represented together with the basic configuration of the entire apparatus in a form incorporated in a vacuum freeze-drying apparatus that mainly uses a material to be dried as a pharmaceutical product. To do.

  FIG. 1 is a normal type that is most frequently used. A vapor condensing unit (trap) 101 is a refrigerant direct-cooling type refrigerant dry evaporator, and FIG. 2 is a type that is used partially, and a vapor condensing unit (trap) 102 is It is an “indirect heat medium type” by circulation of a heat medium liquid that has already been cooled by the refrigerant in the external heat exchanger 7. The vapor condensing unit (trap) 103 in FIG. 3 is a “three-medium heat exchanger” in which both the refrigerant and the heat transfer liquid circulate.

  In FIG. 1 to FIG. 3, vacuum drying chamber (freezing chamber) 1, vacuum trap chamber 2, main pipe 3a connecting them, main valve 3, vacuum exhaust system 4 and other vacuum systems (contour of vacuum chamber and equipment and piping) Are all indicated by “thin lines”.

  Refrigerating apparatus (including a compressor, an oil separator, a condenser, an intercooler in the case of two-stage compression, etc., and may be a two-stage refrigeration) 11, a sub-refrigeration apparatus 12, and a heat exchanger 7 refrigerant The evaporator 7a, the refrigerant evaporator 8a of the auxiliary heat exchanger 8, the refrigerant evaporator of the refrigerant direct cooling type trap 101, the refrigerant evaporator of the steam condenser (trap) 103 of the three-medium heat exchanger, and the refrigerant system The refrigeration refrigerant circulation system such as the passage, the refrigerant valve 13 and the refrigerant expansion valve 14 (denoted by triangles) is indicated by “broken lines”.

  Hot plate (supplies latent heat necessary for drying to the object to be processed, and also serves as a plate for supplying cold heat necessary for preliminary freezing of the object to be processed in the examples of FIGS. 1 to 3), heating medium liquid heater 6, and the above. The heat transfer liquid system 7b of the heat exchanger 7, the heat transfer liquid system 8b of the auxiliary heat exchanger 8, the heat transfer liquid system path of the indirect heat transfer liquid condensing unit (trap) 102, and the heat exchange between the three mediums The heat condensate steam trap (trap) 103 heat medium liquid path, and the heat plate liquid heat pump 9 and the heat condensator (trap) heat medium pump 10 and the like. It is indicated by “thick line”.

  In FIGS. 2 and 3, 15 is a gate valve provided in the circulation system of the heat transfer fluid, but the actual order of the piping system of each system, the various valves, and the device arrangement in the system is not necessarily shown. Rather than being as shown, the figures are simplified for the purpose of describing the prior art disclosed in US Pat. No. 1177616 and the prior art disclosed in US Pat. No. 3,644,845.

  4 and 5 are vertical cross-sections (cross-section AA in FIG. 5) and cross-sections of the vacuum trap chamber 2 and the steam condenser (trap) 103 of the vacuum freeze dryer of the three-medium heat exchanger shown in FIG. 4 (cross-section CC in FIG. 4), the “fine broken line” inside the vapor condensation plate a in FIG. 4 is the flow path of the refrigerant R [the refrigerant pipe indicated by reference numeral 26 in FIG. 6], and the “rough broken line” is At a boundary that divides the flow path (passage w) of the heat transfer liquid in the vapor condensing plate a in a direction orthogonal to the axial direction of the refrigerant pipe 26 (corresponds to a partition wall indicated by reference numeral 27 parallel to the refrigerant pipe 26 in FIG. 6). FIG. 6 is a sectional view of a part of the vapor condensation plate a.

  In addition to the state shown in FIG. 4, the vapor condensing plate a of the three-medium heat exchange type (triple type) air condensing unit (trap) 103 forms the inner wall surface of the vacuum trap chamber 2 in a cylindrical shape as shown in FIG. However, in any case, the refrigerant pipe 26 is welded or pressure-bonded to the vapor condensing plate of the triple vapor condensing device (trap) 103. In addition, the vapor condensing plate a of the triple vapor condensing unit (trap) 103 plays a role of a heat transfer fin of the refrigerant R. The refrigerant R and the heat transfer liquid B exchange heat through the pipe wall of the refrigerant pipe 26 and a steam condenser (trap) 103 as a fin plate, and the heat transfer liquid B and the vacuum vapor V (water vapor) are converted into the heat transfer liquid. Heat is exchanged through the vapor condensing plate a of the vapor condensing unit (trap) 103 which is a wall, and the refrigerant R and the vacuum vapor V are vapors of the vapor condensing unit (trap) 103 which is a heat transfer fin of the refrigerant tube 26. Heat is exchanged through the condensation plate a. Thus, heat exchange between any two of the three media (refrigerant R, heat transfer fluid B, vacuum vapor V) is performed by the boundary metal wall or fin plate. Reference numeral 28 denotes an outer wall of the vacuum trap chamber 2.

  As shown in FIG. 1 to FIG. 3, a vapor condensing unit (trap) of a vacuum apparatus has conventionally been provided with a refrigerant evaporator of a refrigeration apparatus in a vacuum trap chamber. Type steam condensing device 101 "or a trap heat medium including a heat exchanger 7 (hereinafter referred to as cooler 7) having a refrigerant evaporator 7a as a cooling source and a trap heat medium circulation pump 10 as shown in FIG. The intermediate fluid circulation circuit circulates the heat medium liquid cooled by the external cooler outside the vacuum trap chamber 2 to the “indirect heat medium type steam condenser 102” in the vacuum trap chamber 2, or as shown in FIG. It seems that there is a “three-medium heat exchanger” in which both the refrigerant and the heat medium circulate inside.

  The first type using the "coolant direct cooling type" vapor condensing unit (trap) 101 lacks operational stability, is difficult to maintain, is difficult to control temperature, and is added to the heating system. In particular, there is a disadvantage that a sub refrigeration apparatus and a sub heat exchanger are required. In the second embodiment using the “indirect heat medium type” steam condenser (trap) 102, the disadvantage of the first embodiment is improved, but the cooling source refrigerant and the trap condensation surface are provided. First heat loss due to indirect heat transfer from the intermediate fluid heat medium to the trap condensation surface, and heat from the refrigerant evaporator 7a to the heat medium liquid in the external heat exchanger 7 In order to improve the exchange, to increase the heat transfer coefficient on the heat medium side, and to transport the heat medium liquid cooled by the external heat exchanger 7 to the indirect heat medium liquid type vapor condensing unit (trap) 102 Therefore, there is a second heat loss for requiring a large capacity heat medium circulation pump 10 to keep the temperature difference between the entrance and exit of the steam condenser (trap) 102 small, and in addition to the vacuum trap chamber 2 Outside including large heat exchanger 7 and heat medium circulation pump 10 For providing a pipe means comprises a thermal medium of equipment and the partition valve 15, various equipment devices for heat intrusion from the outside, the occupied area was to have a disadvantage of increasing the driving energy.

  A third embodiment using a triple steam condensing unit (trap) 103 which is a “three-medium heat exchanger” is the invention of the above-mentioned Japanese Patent No. 1177616 previously developed by the present applicant (hereinafter referred to as “preceding”). And the invention of Japanese Patent No. 3644845 (hereinafter referred to as the prior invention), as shown in FIG. 3, by providing a trap-type heat transfer medium liquid circulation circuit as in the second embodiment described above, The disadvantage of the direct-cooled refrigerant trap 101 is improved, and a heat exchanger for the refrigerant evaporator and the heat transfer liquid is installed in the vacuum trap chamber 2, and steam is supplied to the other party from either side. With the triple heat exchange steam condensing unit (trap) 103 that is cooled without passing through the medium, various defects of the “indirect heat medium type” steam condensing unit (trap) of the second type are improved. Yes, already true Freeze-drying apparatus to spread, especially in Japan, the mainstream of the position to replace the bimodal conventional refrigerant direct cooling type indirect heat medium type described above.

  The third type vapor condensing unit (trap) 103 of the prior invention and the prior invention, which is the third form, is one of the two media among the refrigerant, the heat transfer liquid, and the vacuum vapor (water vapor). It is a three-medium heat exchanger where there is direct heat exchange between the boundary metal wall or the metal plate in close contact with the boundary metal wall, but when condensing the vacuum vapor, the amount of cold heat necessary for condensation is A part of the refrigerant evaporates from the refrigerant evaporating pipe (refrigerant pipe 26) directly exchanges heat with the vacuum vapor on the condensation surface of the vapor condenser (trap) 103, and a part of the vapor condenser ( It is transmitted to the vacuum vapor on the condensation surface of the trap. Therefore, the condensation capacity of the vapor condenser (trap) of the vacuum vapor is directly related to the amount of heat exchange with the vacuum vapor through the circulating vapor and the amount of heat transfer with the vacuum vapor directly from the refrigerant evaporation pipe (refrigerant pipe 26). In addition, the amount of heat transfer through the circulating heat medium is related to the film heat transfer coefficient of the heat medium liquid.

  However, the vapor condensing plate a of the triple-type vapor condensing device (trap) 103 of the preceding prior invention has an excessively close contact surface between the refrigerant tube 26 of the refrigerant evaporator and the vapor condensing plate a which is a metal plate. The amount of heat exchange with the vacuum vapor V is small due to the direct expansion, and a large amount of refrigerant cooling heat is transferred to the vacuum vapor V on the condensation surface of the vapor condensation plate a of the vapor condenser (trap) 103 via the circulating heat medium liquid B. heat.

  By the way, in recent years, silicone oil is used as the circulating heat transfer liquid B in a vacuum freeze-drying apparatus that uses a drug as an object to be processed. The heat transfer fluid B of the silicone oil has a high viscosity at a low temperature, and the film heat transfer coefficient of the heat transfer fluid B is reduced. Therefore, as shown in FIG. 8, the vapor condensing plate a has a gap between the holding rods 29 in the direction perpendicular to the refrigerant pipe 26 so as to divide the passage w vertically in the passage w of the heat transfer liquid B. Two refrigerant pipes 26 are respectively arranged above and below each of the refrigerant pipes 26 and supported by the holding rods 29, and a total amount of four refrigerant pipes 26 are used. The shortage of the heat exchange area with the heat medium liquid B is compensated. Therefore, the heat exchange via the circulating heat medium has the disadvantage that the temperature difference loss through two boundary film heat transfer increases, and with the strengthening of refrigerant chlorofluorocarbon regulations of the refrigeration system, the two-stage compression type The minimum freezing temperature of the refrigeration system is high, heat transfer temperature difference loss of several degrees Celsius due to the low heat transfer amount of direct cooling, the decrease in the film heat transfer coefficient of the circulating heat transfer liquid B and the limitation of new refrigerant This is difficult for a low temperature trap of −70 ° C. or lower which is particularly required for a vacuum freeze-drying apparatus.

  In addition, the triple steam condensing unit (trap) 103 uses a circulation pump 9 as a driving force for circulating the heat medium liquid B in the heat medium circuit. Of course, in this means, the required capacity of the circulation pump 9 is smaller than the required circulation pump of the conventional indirect heat medium type steam condenser (trap) 102, but the heat input loss due to the heat generated by the circulation pump. If there was. However, in the triple-type steam condenser (trap) 103 manufactured in the preceding invention, the flow path area on the heat medium side is excessive, and in order to secure a necessary film heat transfer coefficient, in particular, silicone is used as the heat medium. What is used as the liquid B needs to increase the capacity of the circulation pump. For this reason, the amount of effective cold heat of the refrigerant is reduced due to the heat input loss due to the circulation pump, which is disadvantageous for the condensation capacity and ultimate temperature of the steam condenser (trap).

  The prior invention improves the direct contact heat transfer reduction of the refrigerant pipe 26 of the trap 103 in the prior invention, and the elliptical long axis of the cylindrical tubular refrigerant pipe 26 made of a metal material is parallel to the condensation collection surface. The flat elliptical pipe 16 having a shape is deformed, and one or both of the pair of flat surfaces formed by the deforming process are brought into close contact with the ceiling wall 17 or the bottom wall 18 of the inner wall surface of the passage w of the heat transfer liquid B. By charging into the passage w as a state, the contact area between the refrigerant pipe 26 that is the elliptical pipe 16 and the inner wall surface of the passage w of the heat transfer liquid B in the vapor condensing plate a is increased, thereby improving the heat transfer performance. Improvement, reduction of transmission temperature difference loss between the refrigerant and the vacuum vapor on the condensation surface, and at the same time increase of the film heat transfer coefficient of the circulating heat medium can be achieved.

However, in this prior invention trap, the refrigerant tube 26 is formed into a flat elliptic tube 16 having a major axis in the left-right direction and a minor axis in the vertical direction when viewed in the axial direction, but the peripheral wall surface is smooth and smooth. When the refrigerant R evaporates in the refrigerant pipe 26, the heat transfer of nucleate boiling decreases, and the circulating heat medium is an elliptical pipe 16 in the passage w of the heat transfer liquid B outside the refrigerant pipe 26. The fluid flows in a laminar flow along the outer surface. The velocity boundary layer and the temperature boundary layer of the heat transfer liquid B formed on the surface of the refrigerant pipe 26 are thick, the convective heat transfer coefficient is reduced, and the refrigerant in the refrigerant pipe 26 and the heat transfer liquid B outside the refrigerant pipe 26 are reduced. The overall heat transfer coefficient has decreased and the heat exchange performance has decreased. Therefore, as a shelf cooler at the time of preliminary freezing, the cooling rate is slow, and the shelf arrival temperature increases due to the increase in the heat transfer temperature difference. As a vapor condensing device during sublimation, there is a problem that the temperature of the heat medium is high, the trap condensing ability is lowered, and the ultimate temperature is also high.
Japanese Patent No. 1177616 Japanese Patent No. 3644845

  The problem to be solved in the present invention is that the overall heat transfer coefficient between the refrigerant in the refrigerant pipe 26 and the heat medium liquid outside the refrigerant pipe 26 is reduced, and the heat exchange performance is lowered, which should be improved. Therefore, the heat transfer of the refrigerant nucleate boiling in the refrigerant pipe 26 and the boundary film heat transfer of the heat transfer medium liquid outside the pipe are greatly increased, and a method for accelerating the heat transfer is sought. From this, the heat transfer of the refrigerant nucleate boiling in the refrigerant pipe 26 of the trap 103 in the prior invention is doubled so that the production of the vapor condensation plate a of the trap 103 is not difficult, and the heat transfer liquid B outside the refrigerant pipe 26 Disturbs the laminar boundary layer of the fluid, causing turbulent flow and doubling the convective heat transfer of the heat transfer liquid B, improving the heat transfer performance, reducing the transfer temperature difference loss between the refrigerant and the vacuum vapor on the condensation surface, and good heat transfer The purpose of the present invention is to provide a steam condensing unit in a vacuum drying apparatus having high performance and high efficiency steam condensing ability.

  In the present invention, as means for solving the above-described problem, a cylindrical tube-shaped refrigerant pipe 26 made of a metal material for evaporating the refrigerant R led from the refrigeration apparatus 11 is formed in the vapor condensation plate a made of a metal material. The heat exchanger 103 is inserted into the passage w of the heat medium liquid B and performs heat exchange between the refrigerant R and the heat medium liquid B, and the heat exchanger 103 is disposed inside the vacuum chamber 1. Alternatively, on the inner wall surface, all or part of the outer surface on the vacuum space side of the heat exchanger 103 faces the vacuum space, and the outer surface on the vacuum space side is on either side of the refrigerant R or the heat transfer liquid B. Also, the structure is cooled directly or by direct metal contact, and the outer surface on the vacuum space side of the heat exchanger 103 is used as a condensation collecting surface of the vacuum vapor V, so that the refrigerant R, the heat transfer liquid B, and the vacuum vapor V are used. Boundary metal between any two of the three media Or in the form of a three-medium heat exchanger in which direct heat exchange exists through a metal plate in close contact with the boundary metal wall, and in the vapor condensing plate a in which the refrigerant pipe 26 is fitted in the vapor condensing unit of the vacuum apparatus A turbulent flow generator z that creates a turbulent flow in the heat transfer liquid B flowing in the passage w is formed in a cross-shape that crosses the passage w, with a narrow interval in the longitudinal direction of the passage w. The present invention proposes a vapor condensing unit in a vacuum apparatus characterized in that a large number of them are juxtaposed and mounted on the left and right or upper and lower partition walls of the passage w.

  In the present invention, the film heat transfer coefficient of the heat transfer liquid B in the steam condensing plate a is greatly increased to promote heat transfer. Therefore, a cross-shaped traverse crossing the passage w in the steam condensing plate a. A large number of turbulent flow generators z formed in parallel are provided in parallel with a narrow interval in the longitudinal direction of the passage w, and the heat transfer liquid flowing through the passage w outside the refrigerant pipe 26 by the turbulent flow generators z is provided. Since the laminar boundary layer is disturbed, the turbulent flow is caused, and the velocity boundary layer and the temperature boundary layer of the heat transfer liquid B are reduced to increase the boundary film heat transfer coefficient. Remarkably improved. This effect was confirmed from the cooling performance test of the steam condensation plate a and the steam condensation performance test during sublimation.

Evaluation of the effect of promoting heat transfer of the vapor condensing plate a by means of forming an uneven portion y in which a large number of grooves or a large number of fins continue in the axial direction when viewed in the axial direction on the inner peripheral surface of the refrigerant pipe 26 of the present invention. Therefore, ^two steam condensing plates a for a 2 m ² small freeze dryer were prototyped and the cooling performance was measured, and the overall heat transfer coefficient of the heat transfer medium liquid in the passage outside the refrigerant pipe 26 from the refrigerant in the refrigerant pipe 26 was determined. Thus, it was compared with the heat transfer performance of the steam condensing plate a of the prior invention in which the refrigerant pipe 26 having a smooth inner peripheral surface was incorporated. Even if the same 2m ² device is used with the same refrigerator and three steam condensing plates a of the prior invention are installed and the heat transfer area of the refrigerant pipe 26 is 6.1 m ² , the inner peripheral surface of the refrigerant pipe 26 is smooth. The overall heat transfer coefficient is reduced due to the decrease in the refrigerant nucleate boiling heat transfer and the decrease in the heat transfer fluid film outside the tube, and the heat exchange performance is reduced as a cooler, so the shelf is cooled from 20 ° C to -40 ° C. The time was about 38 minutes and the shelf arrival temperature was -58 ° C. On the other hand, the steam condensing plate a in which the refrigerant pipe 26 having the uneven portion y formed on the inner peripheral surface of the present invention is inserted is reduced to ^two to reduce the heat transfer area of the refrigerant pipe 26 to 3.1 m ^2. However, since both the refrigerant nucleate boiling heat transfer in the refrigerant pipe 26 with the inner surface unevenness part y and the heat transfer liquid boundary film heat transfer outside the refrigerant pipe 26 are increased, the efficiency of heat exchange is improved. The cooling time to 40 ° C. was 28 min, the temperature to −50 ° C. was about 49 min, and the shelf temperature reached about −60 ° C. Assuming that the heat transfer area of the vapor condensing plate a of the present invention and the refrigerant evaporating elliptic tube 16 is half that of the prior invention, and the temperature difference between the heat medium and the refrigerant is the same, the heat exchange amount of the vapor condensing plate a of the present invention. From this actual measurement result that there was more than the trap of the prior invention, it was shown that the overall heat transfer coefficient of the trap of the present invention means more than twice that of the prior invention. In addition, even if the overall heat transfer coefficient is analyzed from the cooling performance test data using the two steam condensing plates a of the present invention, both the nucleate boiling heat transfer on the refrigerant side and the convective boundary film heat transfer coefficient of the heat transfer liquid increase more than twice. did.

  The present invention means that when the vacuum apparatus is a vacuum freeze-drying apparatus that uses an object to be dried as a pharmaceutical product, the entire structure of the apparatus is shown in FIG. The “exchanger” may be configured in the same manner as the vacuum freeze-drying apparatus W used for the steam condenser (trap) 103.

  Further, the vapor condensing unit (trap 103) to be used forms a plate-shaped vapor condensing plate a with a metal material, and the refrigerant pipe 26 is fitted into the passage w of the heat transfer medium liquid formed therein, There is direct heat exchange between any two of the three media of the refrigerant, the heat transfer medium, and the vacuum vapor through the boundary metal wall or the metal plate in close contact with the boundary metal wall. The configuration of the "exchanger type" is the same as that of the steam condensing unit (trap) 103 in the conventional means shown in FIG.

  However, it is arranged so as to be fitted along the passage w in the passage w of the heat transfer liquid formed inside the steam condensation plate a made of a metal material constituting the main body of the vapor condenser (trap) 103. The refrigerant pipe 26 is formed by pressing a cylindrical cylindrical pipe made of a metal material forming the pipe along a direction perpendicular to the cylindrical wall thereof, and the wall surfaces facing a pair of the cylindrical walls are flat cylindrical pipes. Crushing so as to be a flat plane perpendicular to the axis of the axis, and forming into an elliptical tube 16 having a substantially elliptical shape in which the major axis is approximately 1.5 times the minor axis when viewed in the axial direction. Is desirable.

  When the refrigerant pipe 26 is formed into an elliptical pipe 16 having a flat cross section, the refrigerant pipe 26 is placed in the passage w of the heat transfer liquid formed inside the vapor condensation plate a, and the flat plane is the vapor condensation plate. It is inserted so as to be parallel or substantially parallel to the vacuum vapor condensation collecting surface of a, and one or both of the pair of flat surfaces is brought into close contact with the ceiling wall 17 and the bottom wall 18 of the inner wall surface of the passage w. Join and adhere by welding or crimping.

  At this time, the passage w of the heat transfer liquid B formed in the steam condensing plate a is made of a circular pipe in the same manner as the passage w formed in the steam condensing plate a of the conventional means as shown in FIG. You may form in the dimension shape which reduced the cross-sectional area according to the compressed dimension.

  When the passage w is formed in the shape in which the refrigerant pipes 26 are arranged in parallel in the width direction and four refrigerant pipes 26 are inserted, the middle of the passage w in the longitudinal direction of the passage w. As shown in FIG. 8, the presser bar 29 is disposed at an appropriate position in such a manner as to divide the passage w into two in the vertical direction, and thereby the axial direction of the refrigerant pipe 26 fitted in the passage w. By supporting the intermediate portion, the degree of adhesion of the refrigerant pipe 26 to the inner wall surface of the passage w can be increased. Further, since the cross-sectional area of the passage w can be compressed, the flow rate of the heat transfer liquid B circulated in the passage w can be increased, and the circulation pump having a small capacity can be used.

  A turbulent flow generator z is disposed in a passage w formed inside the vapor condensation plate a. The turbulent flow generator z generates a turbulent flow in the heat transfer medium B flowing in the passage w, and disturbs the flow to thereby form a layer of the heat transfer liquid B on the outer surface of the refrigerant pipe 26 in the passage w. By disturbing the flow, the heat transfer performance is improved by improving the decrease in nucleate boiling heat transfer in the refrigerant pipe 26 and the decrease in the boundary film heat transfer of the heat transfer liquid B outside the refrigerant pipe 26. Yes, as long as it is located in the flow of the heat medium liquid B and causes turbulent flow in the flow, the shape may be appropriately formed.

  The installation interval when the turbulent flow generator z that causes turbulent flow is installed in parallel with the flow of the heat transfer liquid B flowing through the passage w is also the boundary film heat transfer coefficient of the heat transfer liquid B in the steam condensing plate a. It also affects the flow pressure loss of the heat transfer liquid B in the passage. When the interval is large, the flow pressure loss of the heat transfer liquid B can be reduced, but the disturbance of the flow of the heat transfer liquid B outside the refrigerant pipe 26 is reduced and the effect of promoting heat transfer is not so much. If the interval is small, the flow pressure loss of the heat medium liquid B greatly increases, the circulation flow rate of the heat medium liquid B by the heat medium pump 10 decreases, the flow rate of the heat medium liquid B decreases, and the outside of the refrigerant pipe 26 Even if the fluidized boundary layer of the heat transfer liquid B is disturbed, the heat transfer of the heat transfer liquid B is not promoted due to a decrease in the flow velocity, which has an adverse effect. It is necessary to install the turbulent flow generators z at appropriate intervals. The relationship between the flow pressure loss of the heat transfer liquid B and the installation interval of the turbulent flow generator z is evaluated simultaneously with the evaluation of the heat transfer enhancement effect of the steam condensing plate a of the present invention, and the steam condensing plate a of the embodiment of the present invention means. A device for measuring the pressure loss of the heat transfer fluid with the same flow area as the passage of the test was manufactured, and the relationship between the pressure loss, the flow rate of the heat transfer fluid B, and the installation interval of the turbulent flow generator z was tested. As a result, when the viscosity of the heat transfer liquid is 50 cs at 30 ° C., the pressure loss at the bar interval of 40 mm is increased by about 20% from the interval of 80 mm, and the pressure loss at the bar interval of 120 mm is about 30% from the interval of 80 mm. As a result, the pressure loss with the bar spacing of 160 mm became almost the same as the spacing of 120 mm. When the viscosity of the heat transfer liquid is 2 cs at 30 ° C., the pressure loss at the bar spacing of 40 mm is increased by about 28% from the spacing of 80 mm, and the pressure loss at the spacing of 120 mm is reduced by about 20% from the spacing of 80 mm. The loss was reduced by about 40% at 80 mm spacing. From this, when considering both the heat transfer promoting effect of the heat transfer liquid and the reduction of the flow pressure loss, the appropriate interval between the presser bars is in the range of 70 mm to 90 mm with a width of 10 mm before and after the 80 mm as a reference. Is appropriate.

  From this, the turbulent flow generator z is formed in a rod shape that does not cause a large resistance to the flow of the heat transfer liquid B, and is formed in a number of lines at a narrow interval of about 80 mm, in the longitudinal direction of the passage w. It is effective to arrange them in parallel with each other in the shape of a crossing across the passage w.

  At this time, the turbulent flow generators z arranged in parallel may be attached so as to cross over the ceiling wall 17 and the bottom wall 18 of the passage w in the steam condensation plate a as shown in FIG. In addition, when the steam condensing plate a is in the form of a plurality of stacked layers as shown in FIG. 12, the rod-shaped turbulent flow generator z is assembled so as to pass through them vertically. You can do it.

  Further, when the turbulent flow generator z is formed in a rod shape and disposed in a posture along the left-right direction so as to partition the passage w vertically in the passage w in the steam condensation plate a, Of the many parallel turbulent flow generators z, an appropriately selected one is brought into contact with the refrigerant pipe 26 fitted in the passage w and also serves as a pressing rod 29 for supporting it. Is possible.

  Further, the refrigerant pipe 26 fitted into the passage w in the vapor condensing plate a has an uneven portion made up of a large number of grooves or a large number of fins in the axial direction as shown in FIG. Forming y in a shape continuously formed in the axial direction is effective in improving the decrease in nucleate boiling heat transfer of the refrigerant R in the refrigerant evaporation elliptic tube 16.

  The turbulent flow generator z disposed in the passage w in the steam condensing plate a is for disturbing the flow of the heat medium liquid B flowing in the passage w to promote heat transfer. Since the flow rate of the liquid B is hindered and the convection heat transfer liquid transfer of the heat transfer liquid B is adversely affected, it is formed into a round bar shape with low resistance and a large number of lines are installed in parallel at a narrow interval. To do. It is appropriate to set the interval to about 70 mm to 90 mm inside and outside 80 mm.

  And this turbulent flow generator z is arranged at a close position not contacting the refrigerant pipe 26 in the passage w, and is provided so as to be bridged between the ceiling wall 17 and the bottom wall 18 of the passage w, It is effective to disturb the laminar flow of the heat transfer liquid B formed on the outer peripheral surface of the refrigerant pipe 26 to improve the convection heat transfer liquid transfer.

  Further, when the turbulent flow generator z is formed into a rod shape and is provided in the passage w so as to be bridged between the left and right wall surfaces of the inner wall surface of the passage w as shown in FIG. Since it is possible to serve also as a pressing rod 29 for supporting the refrigerant pipe 26 fitted in w, the one appropriately selected from the turbulent flow generators z provided in parallel with a narrow interval, The pressure bar 29 may be omitted in contact with the refrigerant pipe 26 in the passage w.

  The above-described uneven portion y provided on the inner peripheral surface of the refrigerant pipe 26 is for improving the nucleate boiling heat transfer of the refrigerant R in the refrigerant pipe 26, and is axially provided on substantially the entire inner peripheral surface of the refrigerant pipe 26. A large number of V-grooves are arranged in parallel in the circumferential direction when viewed, or the grooves are formed in a form that is continuous in the axial direction, or a large number of fins are arranged in parallel in the circumferential direction when viewed in the axial direction. It is desirable to form in a continuous form.

  Next, embodiments will be described in detail with reference to the drawings. In addition, the same code | symbol shall be used for a structural member similar to the thing of the conventional means for drawing.

  FIG. 9 is a longitudinal sectional view of a steam condensing plate a constituting a portion of a steam condensing unit (trap) 103 installed in a vacuum apparatus for carrying out the prior invention. In the figure, a is a plate made of a metal material. The formed steam condensing plate, w is a passage formed inside the steam condensing plate a, B is a heat medium liquid circulated in the passage w, 26 is a refrigerant pipe inserted through the passage w, and R is The refrigerant to be circulated in the refrigerant pipe 26 is shown. The refrigerant pipe 26 is deformed into an elliptical pipe 16 and has an uneven portion y provided with a large number of grooves or fins on its inner peripheral surface.

  The vacuum apparatus in this example is a vacuum freeze-drying apparatus mainly for the drying process of pharmaceuticals shown in FIG. 3, and a vapor condensing device (trap) incorporated in the vacuum apparatus is indicated by reference numeral 103 in FIG. The three-medium heat exchanger type steam condenser (trap), and the basic configuration of the vacuum apparatus and the steam condenser (trap) 103 is that of the conventional means described in FIGS. And there is no change.

  Further, the passage w of the heat medium B formed inside the vapor condensing plate a is based on the passage w formed so as to be inserted through the two refrigerant pipes 26 as the conventional cylindrical pipe shown in FIG. The cylindrical refrigerant tube 26 is compressed by approximately 60 to 70% by the amount corresponding to the compression of the cylindrical refrigerant tube 26 into the elliptical tube 16.

  The refrigerant pipe 26 inserted and installed in the passage w is formed by pressing the cylindrical tubular refrigerant pipe 26 used in the conventional means into an elliptical pipe 16 having a flat cross section by pressing, and has a long axis. On the other hand, it is molded so that the minor axis is approximately 3/5.

  Next, FIG. 10 shows another embodiment. In this example, the refrigerant pipe 26 is deformed into an elliptical pipe 16 and is inserted into the passage w, and the turbulent flow is used to promote heat transfer of the heat transfer liquid B and support the refrigerant pipe 26 at regular intervals in the passage w. This is an example in which the generator z is installed, and the refrigerant pipe 16 with the concavo-convex portion y is inserted into the inner surface of each two on the upper surface side and the lower surface side thereof, and the passage w is located above and below the passage of the conventional means. The height (the dimension in the thickness direction of the steam condensing plate a) is formed to be approximately 3/5.

  The refrigerant pipes 26, which are the elliptical pipes 16 with the inner surface irregularities y inserted into the compartments of these passages w, pass through one of the flat surfaces 16a in the passage w. In this case, the flat surface 16a is in close contact with the bottom wall 18 of the passage w.

  Next, FIG. 11 is a conceptual diagram of the heat flow when the above-mentioned steam condensing plate a condenses water vapor. Of the heat flow crossing the plate width L from the vapor condensation surface (ice surface) of the vapor condensation plate a, part of the heat flow Q1 flows into the refrigerant pipe 26 by direct conduction (via contact resistance), part of which is the width L1. The width L of the heat flow Q2 reaching the refrigerant pipe 26 through the boundary film heat transfer of the heat transfer liquid B circulating through the passage w from the vapor condensation plate a, and the contact surface width between the refrigerant pipe 26 and the vapor condensation plate a are assumed to be ε.

  On the other hand, the heat flow Q1 flowing directly into the inner grooved refrigerant pipe 26 by direct conduction is involved in the following thermal resistance. That is, the thermal resistance R13 of the condensed ice layer, the thermal resistance R12 to the contact surface width ε through the plate thickness of the vapor condensation plate a, the contact thermal resistance R11, and the heat transfer resistance R10 of the refrigerant in the refrigerant pipe 26. . Among them, the contact thermal resistance R11 is greatly influenced by the contact surface width ε and the equivalent contact gap δ between the refrigerant pipe 26 and the vapor condensation plate a. The heat transfer resistance R10 of the refrigerant is related to the nucleate boiling heat transfer coefficient in the pipe.

  In the vapor condensing device (trap) 103 according to the present invention, the contact surface width of the refrigerant tube 26 formed as the elliptic tube 16 with the flat inner surface uneven portion y is considerably increased as compared with the refrigerant tube 26 formed as a cylindrical tube. Refrigerant tube 26 with inner surface unevenness portion y has a small resistance, and the nucleate boiling heat transfer coefficient of the refrigerant is 2.3 times, the heat transfer resistance R10 of the refrigerant is also reduced to less than half, and the refrigerant evaporation tube is directly conducted. The heat flow Q1 transferred to increases.

  On the other hand, the thermal resistance of the heat flow Q2 reaching the refrigerant pipe 26 with the inner surface uneven portion y via the circulating heat medium liquid B is the thermal resistance R24 of the condensed ice layer, the thermal resistance R23 penetrating the plate thickness, The boundary film heat transfer resistance R22 at the interface between the (including partition) and the heat transfer liquid B, the boundary film heat transfer resistance R21 around the refrigerant pipe 26 with the inner surface uneven portion y (excluding the contact surface width ε), and the refrigerant pipe 26 It is comprised by the heat transfer resistance R20 of the inside refrigerant | coolant. Among them, the film heat transfer coefficient of the circulating heat transfer liquid B has a great influence on the thermal resistances R22 and R21. The promotion of the film heat transfer coefficient increases the heat flow through the circulating heat medium. As a result of theoretical analysis and test evaluation of the heat transfer performance of the steam condensing plate a which is the trap 103, the trap 103 of this embodiment has the film heat transfer coefficient of the heat transfer liquid B by arranging the turbulent flow generators z at appropriate intervals. Was 2.7 times that of the prior invention, a significant improvement. In the prior invention trap, the heat transfer liquid in the passage w flows in parallel along the surface of the refrigerant pipe 26, the boundary layer is thick and heat transfer is reduced, and the present invention is provided with a turbulence promoting rod that disturbs the boundary layer. As a result, both a cross flow and a parallel flow were generated on the surface of the refrigerant pipe 26, and the film heat transfer of the heat transfer liquid was greatly accelerated. The overall heat transfer coefficient from the refrigerant in the refrigerant pipe 26 to the trapped ice layer surface is larger than that of the trap of the prior invention, and the heat transfer performance is increased by about 1.5 times in the initial stage of freeze-drying. However, the overall heat transfer coefficient increased by about 100%.

  Further, in this embodiment of the present invention, the trap 103 is manufactured by the refrigerant pipe 26 with the inner surface uneven portion y, and the inner passageway w of the vapor condensing plate a is manufactured thin like the trap of the prior invention, The flow path area on the medium side is reduced, the flow on the heat medium side is promoted, the arrangement of the turbulent flow generator z is added, and the film heat transfer performance is further improved. Although the heat medium pressure in the passage w is increased by the arrangement of the turbulent flow generator z, the heat medium boundary film is reduced even if the heat medium circulation amount is decreased to be equal to the heat medium pressure loss of the prior invention trap. The heat transfer coefficient increases. Therefore, the capacity of the circulating pump 10 for the heat transfer liquid can be reduced, and the heat input loss is reduced due to the heat generated by the pump.

  In addition, since the trap heat transfer and condensation performance is increased more than double that of the prior invention trap, the number of traps can be reduced and the manufacturing cost can be reduced.

  As described above, in this embodiment of the present invention, the refrigerant pipe 26 inserted into the passage w in the vapor condensing plate a of the refrigerant evaporator is changed from a smooth pipe having a smooth peripheral surface to an elliptic pipe 16 with an inner surface uneven portion y. Since the processed flat surface is in close contact with the inner wall surface of the passage w, the contact surface between the refrigerant pipe 26 and the vapor condensing plate of the metal material is sufficiently increased, and the contact thermal resistance can be greatly reduced. In addition, the elliptical refrigerant pipe 26 is a cylindrical pipe with an inner surface uneven portion y, pressed, and processed into a flat shape, so that an optimum long and short axis refrigerant pipe can be easily obtained. At this time, since the cross-sectional area thereof is almost the same as that of the cylindrical tube, the trap can be easily manufactured.

  Further, the turbulent flow generators z arranged in parallel at equal intervals along the refrigerant pipe 26 charged in the passage w of the heat medium liquid B disturb the laminar flow on the outer surface of the refrigerant pipe 26 and thereby the heat medium liquid B. The convection film heat transfer of the refrigerant is promoted, and both the nucleate boiling heat transfer on the refrigerant side and the convection film heat transfer coefficient of the heat transfer liquid are increased more than twice, so the vacuum device has good heat transfer performance and high efficiency steam condensation ability. A new steam condensing unit will be obtained.

It is a general | schematic explanatory drawing of the conventional vacuum apparatus which used the refrigerant | coolant direct cooling type | mold trap for the trap. It is outline | summary explanatory drawing of the conventional vacuum apparatus which used the indirect-heat-medium type | mold trap for the trap. It is outline | summary explanatory drawing of the conventional vacuum apparatus which used the heat exchanger between three media for the trap. It is the front view which carried out the longitudinal section of the trap chamber and trap of a vacuum device same as the above. It is the side view which carried out the longitudinal section of the trap chamber and trap of a vacuum device same as the above. It is a longitudinal cross-sectional view of the trap part same as the above. It is a longitudinal cross-sectional view of the trap chamber of another form of a vacuum apparatus same as the above. It is a longitudinal cross-sectional view of the trap part of another form of a vacuum apparatus same as the above. It is a longitudinal cross-sectional view of the trap part in the vacuum device by a prior invention. It is a longitudinal cross-sectional view of the part of another Example of the trap in a prior invention. It is heat flow explanatory drawing at the time of condensation of a trap in a prior invention. FIG. 6 is a plan view of another embodiment of a trap according to the present invention. Partial longitudinal section of a trap according to the invention Partial plan view of a trap according to the invention FIG. 5 is a partial longitudinal sectional view of another embodiment of the trap according to the present invention.

Explanation of symbols

  B ... Heat transfer liquid, R ... Refrigerant, V ... Vacuum vapor, W ... Vacuum freeze-drying device, a ... Vapor condensation plate, b ... Vapor collecting surface, w ... Passage, y ... Uneven portion, z ... Turbulence generator DESCRIPTION OF SYMBOLS 1 ... Vacuum-drying chamber, 10 ... Heat-medium circulation pump, 101 ... Refrigerant direct cooling trap, 102 ... Indirect heat-medium trap, 103 ... Trap also serving as a heat exchanger, 11 ... Refrigerating device, 12 ... Sub-refrigerating device, DESCRIPTION OF SYMBOLS 13 ... Refrigerant valve, 14 ... Refrigerant expansion valve, 15 ... Gate valve, 16 ... Refrigerant evaporation elliptical tube, 16a ... Flat surface, 17 ... Ceiling wall, 18 ... Bottom wall, 2 ... Vacuum trap chamber, 26 ... Refrigerant tube, 27 DESCRIPTION OF SYMBOLS ... Partition wall, 28 ... Outer wall, 29 ... Holding rod, 3 ... Main valve, 3a ... Main pipe, 4 ... Vacuum exhaust system, 5 ... Heat plate, 6 ... Heating medium liquid heater, 7 ... Heat exchanger, 7a ... Refrigerant Evaporator, 7b ... Heat medium liquid system, 8 ... Sub heat exchanger, 8a ... Refrigerant evaporator, 8b ... Heat medium liquid system, 9 ... Heat medium liquid circulation port Flop.

Claims (4)

  A cylindrical tube-shaped refrigerant pipe 26 made of a metal material for evaporating the refrigerant R led from the refrigeration apparatus 11 is fitted into a passage w of the heat transfer liquid B formed in the vapor condensation plate a made of the metal material, and the refrigerant R The heat exchanger 103 that performs heat exchange between the heat transfer medium B and the heat exchanger liquid B is configured, and the heat exchanger 103 is disposed on the inside or the inner wall surface of the vacuum chamber 1 on the vacuum space side outer surface of the heat exchanger 103. Is provided so that all or part of it faces the vacuum space, and the outer surface on the vacuum space side is cooled from either side of the refrigerant R or the heat transfer medium B directly or by direct metal contact. The outer surface on the vacuum space side of the heat exchanger 103 is used as a condensation collecting surface of the vacuum vapor V, and between any two of the three media of the refrigerant R, the heat medium liquid B, and the vacuum vapor V. Direct heat through the boundary metal wall or metal plate in close contact with the boundary metal wall In the vapor condensing unit of the vacuum apparatus, the heat medium liquid B flowing through the passage w is formed in the passage w in the vapor condensing plate a into which the refrigerant pipe 26 is fitted. A turbulent flow generator z that generates turbulent flow is formed in a cross-shape that crosses the passage w, and a plurality of turbulent flow generators z are juxtaposed at a narrow interval in the longitudinal direction of the passage w so as to be arranged between the left and right or upper and lower partition walls A steam condensing unit in a vacuum device, which is mounted on a cross.   The parallel interval of the turbulent flow generators z provided in parallel in the longitudinal direction of the passage w in the passage w in the steam condensing plate a is set to an interval of about 70 mm to 90 mm of about 10 mm before and after 80 mm as a reference. The vapor condensing unit in a vacuum apparatus according to claim 1, wherein the vapor condensing unit is set.   A plurality of the turbulent flow generators z are formed in a rod shape and arranged in parallel in the passage w in the steam condensing plate a with a narrow interval in the longitudinal direction of the passage w, and these turbulent flows are generated. 2. A steam condensing device in a vacuum apparatus according to claim 1, wherein a turbulent flow generating body z appropriately selected from the body z is used as a pressing rod 29 for supporting a refrigerant pipe 26 fitted into the passage w. .   The refrigerant pipe 26 fitted into the passage w in the vapor condensing plate a is provided on the substantially entire inner surface of the inner peripheral wall of the refrigerant pipe 26 so that a large number of grooves or a large number of fins are continuous in the axial direction when viewed in the axial direction. The steam condensing device in the vacuum apparatus according to claim 1, wherein:

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