SU1332135A1 - Method of cooling compressed air in two-section plate-type heat exchanger and plate-type heat exchanger - Google Patents

Abstract

The invention relates to heat engineering and makes it possible to increase the efficiency when using as a cooling medium atmospheric air and the other using water. Collectors 7–10, with additional coolant extraction and removal in adjacent sections, have common dividing walls 15 and 16 with bypass windows 17 and g 18. Overlapping bodies 19 and 20 windows 17 and 18 m. equipped with mechanisms 29 and 30 of reciprocating movement and made in the form of dampers interconnected by means of rods 35 and 56. If the difference t-p of water and air is less than 6-8 С, then the air is passed through the first section of the cooled gas, and through the second - water. When the difference t-p of water and air is more than 6-8 C, air is passed through both sections. J3. The result is the highest thermal efficiency of the heat exchanger during the whole year due to the maximum use of the natural cold of the environment. In addition, the autonomy of parallel connection of both sections of the heat exchanger into one circulation loop and their inclusion in separate circuits with relatively simple constructive execution and reduction of hydraulic resistances is provided. 2 sec. and 7 hp f-ly, 12 ill. W with soyo with SP L 5

Description

The necessity of fulfilling the indicated ratios is clearly confirmed by a graph (Fig. 12), which shows the change in the initial temperatures of the water and atmospheric air, as well as the change in the temperature of the compressed gas after passing through the second section of the heat exchanger when using the atmosphere.

The invention relates to heat exchangers and can be used to effectively cool the compressed gas at various temperatures of cooling media, depending on the season.

The purpose of the invention is an increase in eco-. when it is used as one of the coolants, the atmosphere of air (line I) and water (lifer air, and the other - water. nor II) is used during a year. As seen

FIG. 1 depicts a plate-like graph, to a certain ratio-heat exchanger for cooling the initial atmospheric temperatures of the compressed gas, the first option; more efficient air and water

15 to cool the compressed gas in the second section with atmospheric air (segments AB, C – D), and with decreasing temperature differences Tp and Tp, it is more efficient to wate up with water (segment BC). This 20 position is caused by different magnitude of the amplitude of oscillations of the values of water and atmospheric air temperatures during the year. The ratio of temperatures T P FIG. 7 - a double dividing wall — 25i — which requires the replacement of a cooling cage with a closed cavity, inside the co-environment in the second section, which is determined by a shutter located in the form of shutters connected by rods passing through partitions; in fig. 8 - double dividing wall - 30

in fig. 2 - the same, the second option; in fig. 3 shows section A-A in FIG. 1 and 2; FIG. 4 is a section on BB in FIG. one; in fig. 5 - a dividing wall with overflow windows, shut-off bodies in the form of dampers and a reciprocating mechanism; in fig. 6 - a dividing wall with overlapped organs in the form of dampers connected by rods; on

from the equality of the temperatures of the compressed gas after passing through the second section with both cooling options

A vessel whose cavity is in communication with the pipelines, U.TW, and the value of the gas inhaled the compressed gas into the heat exchanger when air and water are used as the cooling medium.

It is known that it is optimal in return ducting of one of the cooling media; in fig. 9 - dividing partition with a flap mounted on the axis of rotation; in fig. 10 - 5

} dividing partition with a mechanism

Shifting of overlapping organs, made in the form of a bimetallic plate;

 in fig. 11-partition wall

, with an overlapping organ in the form of a bimetal-40, the magnitude of the undercooling of the plastic plate is recommended; in fig. 12 - depending on the heat exchanger is the ratio of the change in the initial temperatures of water and atmospheric air, as well as the change in temperature of the compressed gas after passing through the second section when using atmospheric air and water during the year.

The method of cooling compressed gas in a two-section lamellar heat response iT, 6-15 ° C and ДТу, 4-12 ° С Since the highest thermal efficiency at a calculated temperature of 45 atmospheric air is achieved by water cooling, then the heat exchange surface of the second section is specified when used for thermal interaction of comp

A mennike using two different media gQ of that gas with atmospheric air will not be able to provide the recommended values of uTjj as one of them. In connection with this, this value has several initial values, namely 20 C. Then, from equality (1), the following cooling media of atmospheric air with temperature T, and the other with water with temperature T is that under condition C through the first along the cooled gas section air is passed, through the second - water, and when C passes air through both sections.

55

em.

what is VT, 6-8 C.

Therefore, when T., C, it is advisable to cool in both sections with atmospheric air, and when

The necessity of meeting these ratios is clearly confirmed by a graph (Fig. 12), which shows the change in the initial temperatures of the water and atmospheric air, as well as the change in the temperature of the compressed gas after passing through the second section of the heat exchanger when using atmospheric air (line I) and water (line Ii) throughout the year. As seen

to cool the compressed gas in the second section with atmospheric air (segments AB, C – D), and with decreasing temperature differences Tp and Tp, it is more efficient to wate up with water (segment BC). This position is caused by different magnitude of the amplitude of fluctuations of water and atmospheric air temperature values during the year. At the same time, the ratio of temperatures T P which requires replacement of the cooling medium in the second section is determined by

from the equality of the temperatures of the compressed gas after passing through the second section with both cooling options

TO + UT ,,

(one)

where iTd, U.TW are the magnitudes of undercooling of compressed gas in a heat exchanger when using atmospheric air and water as the cooling medium.

It is known that the optimal recommended subcooling value in a heat exchanger is equal to

It is appropriate iT, 6-15 ° С and ДТу, 4-12 ° С. Since the highest thermal efficiency at a design temperature of 45 atmospheric air is achieved with water cooling, then the given presetting heat transfer surface of the second section, when used for thermal interaction of compressing gas from that gas with atmospheric air, cannot provide the recommended values of uTjj. In this connection, the given value has several intrinsic values, namely 20 C. Then, from equality (1) to the next 55

em.

what is VT, 6-8 C.

Therefore, when T., C, it is advisable to cool in both sections with atmospheric air, and when

Tjj С in the first section - by atmospheric air, and in the second - by water. The proposed method is carried out by means of a plate heat exchanger, which contains corrugated plates 1 and 2 located between flat sheets 3 and limited from opposite edges side sealing spacers 4 and 5 with formation of channels for cooled and cooling media, the latter of which are divided by partitions 6, at least two separate cooling sections, enclosed by means of manifolds 7-10 and pipelines 11-14, into separate circulation circuits. The collectors 7-10 have common dividing walls 15 and 16 installed at the level of partitions 6 and equipped with bypass windows 17 and

18c with overlapping bodies 19 and 20, made in the form of dampers. The channels of the cooled medium are connected to the inlet 23 and the outlet 24 gas pipelines via collectors 21 to 22. AT . The temperature collector 7 and the pipe 12 (or only in the collector 7) are equipped with temperature sensors 25 and 26 connected to a signal converter 27, which is connected to a setting device 28. The latter is connected to reciprocating mechanisms 29 and 30, respectively, of the shut-off elements 19 and 20 and mechanisms 31 and 32 of the shut-off valves 33 and 34 (or with a pump). Mechanisms 29 and 30 through rods

35 and 36 are connected to rotating organs 19 and 20. The latter are connected by a rod 37 in a number of cases. When dividing walls 15 and 16 are made double, additional channels 38 and 39 are made with a closed cavity in the wall 16, connecting this cavity to the collector cavity 10 and pipeline 14. Overlap body

19 may be designed as a damper eccentrically mounted on the axis of rotation 40. The mechanism 29 for reciprocating the movement of the closing bodies 19 and 20 relative to the walls 15 and 16 can be performed in

a bimetallic plate 41 bonded at one end with spacers 5 sealing the channels of the medium to be cooled from the supply manifold 7. The closing member 19 from the coolant supply side can be made in the form of a bimetallic plate 42 attached at one end to the dividing wall 1

During operation of the heat exchanger, the compressed gas through the pipe 23 is supplied through the collector 21 to the corresponding channels of the heat exchanger, successively passes through the first and second cooling sections, entering into thermal interaction with the cooling media, goes to the collector 22 and then to the gas pipeline 24. Atmospheric air pipe 11 and the collector 7 is injected into the first cooling section of the heat exchanger, passes it and through the collector 9 is directed to the air duct 13. At the same time, from the temperature sensor 25 installed in the collector 7, eredaets signal to the transmitter 27 from which the signal is transmitted to the dial 28 where it is compared with a signal from pereda.vaemym temperature sensor 26 installed in the pipe 12, or with a predetermined characteristic varying initial water temperature from the initial temperature of air for a given area. In the sensor 28, a command signal is generated which is supplied to the mechanisms 29 and 30 of the movement of the shutters 19 and 20 and the actuators 31

and 32 shut-off valves 33 and 34 (or for a drive, a pump not shown in the drawing). At T, - T, a command signal is generated that overlaps the valves 33 and 34 and moves the shutters 19 and 20 along the partition walls 15 and 16 with the opening of the bypass windows 17 and 18. As a result, part of the cooling air from the collector 7 through the window 17 enters the collector 8, and from there into the cooling channels of the second section. The cooling water remaining in them is forced into the drain line (not shown). Further, atmospheric air enters the collector 10 and then through the window 18 into the collector 9. Thus, the compressed gas is cooled by atmospheric air in the second section.

At TQ i T, -6-8 ° C, a command signal of opposite sign is produced, which actuates the actuators 29-32 of the dampers 19 and 20 and the gates 31 and 32.

As a result, the bypass windows 17 and 18 overlap the valves 19 and 20 and open the valves 31 and 32,. Then, through the pipeline 12, cooling water enters the collector 8, which is then distributed through the channels of the second section and then through the collector. 10 goes into the pipeline 1D.

In the case of using interconnected stem 37 of shut-off bodies 19 and 20, a command signal is applied to one common displacement mechanism 29 and valve actuators. Moreover, when separating walls 15 and 16 are performed by double interceptions of the cooling water discharge pipe 14, the shutter 20 moves. In this case, the window 38 connecting the collector 10 to the pipeline 14 overlaps. Therefore, the command signal from the setting unit 28 is sent only to actuators 29 and 31 (or instead of the latter on the pump drive).

When an organ 19 is mounted on an axis 40 with an offset from its geometric center in the range T - 6-8 ° C, the water entering the collector 8 rotates around the eccentrically installed rotation axis 40 of rotation overlapping member 19 and closes the window 17. Simultaneously with this, the signal supplied from the setpoint 28, provides for the closure of the window 18 and the opening of the discharge pipe 14.

When mechanism 29 is made in the form of a bimetallic plate 41, depending on the temperature of the atmospheric air, the bimetallic plate 41 bends or straightens and provides linear movement of the closing bodies 19 and 20. When reaching

/

(downward) to a certain temperature T. T - 6-8 from window 17 and 18 completely overlap with flaps 19 and 20 and a signal is supplied from a specially installed sensor (not shown) to the actuators of the valves 33 and 34.

When the organ 19 is made in the form of a bimetallic plate 42, the latter, depending on the temperature of the atmospheric air, changes its position by opening or closing the window 17, and the corresponding signal is transmitted to the actuators

the second valve body 20 and the valves 33 and 35.

Using the proposed cooling method and device for its implementation ensures the highest thermal efficiency of the plate heat exchanger during the whole year due to the maximum use of the natural cold of the environment, which reduces the power consumption of the compressor unit, as well as ensures safe working conditions in the hot season. . In addition, the invention allows for the autonomy of parallel connection of both & their heat exchanger sections into one circulation loop and their inclusion into separate circuits with a relatively simple design and reduction of hydraulic resistances, which generally improves efficiency at different ambient temperatures depending on time of year.

Claims (9)

1. A method of cooling a compressed gas in a two-section plate heat exchanger using two different media, in order to increase efficiency when using atmospheric air with temperature T as one of the cooling media and temperature T with the other medium. C, air is passed through the first section along the cooled gas, water passes through the second, and at T –T | 6-8 C through. both sections let air through. 2. A plate heat exchanger containing heat exchanger sections with channels separated by partitions, limited from opposite edges by sealing spacers and connected to the respective pipelines via supply and discharge collectors, characterized in that, in order to increase the efficiency, the collectors Supply and removal of cooling media in adjacent sections have common dividing walls with overflow windows, equipped with overlapping bodies. 7133 3. A heat exchanger according to claim 2, characterized in that it is provided with a mechanism for reciprocating the movement of the shut-off bodies, which are made in the form of dampers. 4. The heat exchanger according to claims 2 and 3, which is characterized by the fact that the dampers are interconnected by means of rods passing through the channels of one of the cooling working media, and connected to the mechanism of reciprocating and pushing one of these stocks. 5. A heat exchanger according to Claims 2-4, characterized in that the partition walls of adjacent collectors are made double with a closed cavity, inside which the dampers are installed, and the last connecting rods are placed inside partitions between the heat exchange sections, 6. Heat exchanger according to claims 2-5, in that the cavity of the separation walls communicates -  , ten 15 20 25 358 on with a collector and a pipeline to drain one of the cooling media. 7. Heat exchanger according to claim 2, wherein the difference is that one of the dampers between the coolant supply collectors is installed on an axis perpendicular to the direction of movement of the media with displacement relative to the geometric center of the flap. 8. Heat exchanger according to claims 2-6, characterized in that the reciprocating mechanism is made in the form of a bimetallic plate installed in the collector to supply one of the cooling media and one end fastened with spacers bounding the channels of the cooled medium. 9. Heat exchanger according to claims 2 and 8, characterized in that the damper between the coolant supply manifolds is made in the form of a bimetallic plate, one end attached to their dividing wall. 1G15 P 12 1 sixteen / 57 9U2. FIG. 6 nineteen at ig.8 hschzr 1c 9i, g. iO 17 fPu2.11 1 l W I W W WE. ISM Months Fig.yy Compiled by Y. Karpenko Editor G. Volkova Tehred M. Khodich Corrector A. Tsko Order 3792/35 Circulation 611 Subscription VNIIPI USSR State Committee for Inventions and Discoveries 113035, Moscow, Zh-35, Raushsk nab. 4/5 Production and printing company, Uzhgorod, st. Project, 4