JPH02504422A - Plate heat exchanger - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed description of the invention] Plate heat exchanger field of invention TECHNICAL FIELD This invention relates generally to heat transfer devices, and more particularly to plate heat exchangers.

The heat exchanger of the present invention is a compressor that efficiently cools compressed gas and utilizes the heat of compression. Its application can be found in subrants.

The invention also provides cooling and heating of the process flow within the air separation unit. Can be used in chemical industry, refrigeration plants, gas industry, machine shops, vehicles etc. Wear.

Background of the invention For what is known as a plate heat exchanger, for example, the Soviet inventor's certificate No. 1,332. There is one disclosed in No. 135. This plate heat exchanger has at least two heat transfer sections. Each heat transfer section has parallel heat transfer plates.

Between these two heat transfer plates, there is a first slit for conveying the first and second heat transfer plates. a first slit-like passage; and a sealing spacer extending across the first slit-like passage. conveying a second fluid medium which is fluidly isolated from the first slit-like passageway by A second thrift-like passageway is formed for the purpose of passing through. The first slit-like passage has two The heat transfer sections run continuously and are structurally structurally consistent throughout their length. similarly configured and for supplying the first fluid medium via the supply header and the discharge header. It communicates with the pipes that supply and discharge the water. Second slit in each heat transfer section The shaped passageway supplies and discharges the second fluid medium through the supply header and the discharge header. It communicates with the pipe.

Uses additional devices to evenly distribute the flow of fluid directed into the passage by the header With regard to the flow of this fluid medium, this known plate heat exchanger does not need to , similar to other heat exchangers, the strength of heat exchange across the silkworm body of the heat exchanger is 1 ntensi ty of heat excbaBe) changes. Also, some parts of the heat exchanger Operation efficiency is not good. This means that the fluid medium flows from the supply header into the first slit-like passage. The fluid medium is unevenly distributed within the first slint-like channel when conveyed to the channel. This is explained by:

Also, in known heat exchangers, a first section of fluid media with different thermal and physical properties is used. Achieving highly efficient heat exchange when used in the cushion and second section I can't.

Most of the reasons for this lack of sufficiently high heat exchange efficiency are, as mentioned above, The first slit-like passages parallel to each other are continuous, and the entire length of the two heat transfer sections is This is due to the fact that it cannot be structurally changed over the period of time. Therefore, two heat transfer The second slit-like passageway in the section is structurally the same. That is, these The second slit-like passage has the same diameter and length, and has the same diameter and length as the surface of the heat transfer plate. a slit formed by surfaces and a corrugated insert interposed between these surfaces; The heat transfer surfaces per unit width of the shaped passages are equal.

However, to achieve highly efficient heat transfer, a second slot in each section is required. With regard to the structural arrangement of the slit-like passages, it is possible to It is necessary to take into account the specific thermal and physical properties of the fluid medium being used. . Therefore, when using fluid media with different thermal and physical properties, the second It is necessary to make the structures of the slit-like passages different from each other. For example, a plate heat exchanger Using atmospheric air in the first heat transfer section as the second fluid medium; Efficient heat transfer in two heat transfer sections when water is used in the To achieve this, the geometry of the heat transfer surface on the air side and the water side must be different. It is necessary to make it happen.

For this purpose, firstly, on the atmosphere side! Let p be the heat transfer coefficient on the water side. It would be necessary to reduce this by a factor of 30-50.

Also, when the first fluid medium flows along the continuous first slit-like passage, this first 1. Due to non-uniform temperature changes in the fluid medium, nuclear heat exchange occurs during operation of the known plate heat exchanger. Large thermal stresses occur in the exchanger.

Finally, in the known plate heat exchanger, the middle part of the first slotted passage 7) of the heat exchanger Although the first fluid medium or its components cannot be intermediately discharged from the In some cases this is required.

For example, a combination refrigerator that cools compressed air, which has been called the first fluid medium, If a known plate heat exchanger is used for the blunt, this compressed air will pass through the first slit. When conveyed along the slit-shaped passages, water is filled on the inner surface of these first slit-shaped passages. Minute condensation occurs. This moisture gradually accumulates in the passageway and forms a film. has an open area and thus adds to the heat transfer from compressed air to other fluid media. thermal resistance occurs, preventing strong heat exchange.

Therefore, in order for a strong heat exchange to take place, the air must pass through the first slit-like passage. It is necessary to drain the water before it flows out.

Summary of the invention Therefore, the object of the present invention is to In order to efficiently exchange heat between the first slotted passages 7), An object of the present invention is to provide plate-shaped heat exchangers that are connected and arranged relative to each other.

The above object of the present invention is to provide at least two heat transfer sections. each of the heat transfer sections includes parallel heat transfer plates; Between these heat transfer plates is a first fluid medium to be conveyed through the heat transfer plates. a first slit-like passage for the body and a second stream to be conveyed through the heat transfer plate; a second slit-like passageway for the body medium; The first slit-like passages are in continuous communication with each other and are connected to the supply header and the discharge header. a pipe for supplying and discharging the first fluid medium through an output header, respectively; while the second slit-like passage of each heat transfer section is in communication with the , extending across the first slit-like passageway and extending from the first slit-like passageway. are fluidly isolated and are connected to each other via a supply header and a discharge header, respectively. A plate heat exchanger connected to a pipe that supplies two fluid media and a pipe that discharges the fluid medium. and between the first slit-like passages of each of the mutually adjacent heat transfer sections. is provided with an intermediate header communicating with these first slit-like passages, and one The first slit-like passage of the heat transfer secretin on the one side is opposite to the first slit-like passage on the other side. In a projection view on a vertical plane, the first slit-like passage of the other heat transfer secretin A plate-shaped heat exchanger characterized by being arranged at an angle to the road. will be achieved.

An intermediate ladder is interposed between adjacent heat transfer sections of the plate heat exchanger of the present invention. Since the first slit-like passages of both heat transfer sections are in communication with each other, the middle Velocity pattern and temperature pattern in the flow of the first fluid medium flowing through the header The flow can be made uniform, so that the first fluid medium is transferred from the ladder to the second to the middle. The heat is distributed evenly by the first slit-like passages of the heat section, and thus the second Heat transfer in the thermal section can be made more efficient.

Also, the temperature pattern in the flow of the first fluid medium within the intermediate header is uniformized. This reduces the thermal stress that occurs in the plate heat exchanger. Also, by providing an intermediate header, the risk of thermal deformation occurring in the first slit is reduced. The first fluid medium in the first part of the net-like passage is mixed, thereby increasing the heat transfer efficiency. You can make it bigger.

Since the plate heat exchanger of the present invention is provided with an additional blower, it is possible to cool the compressed air. If the plate heat exchanger of the present invention is used as a compressor sublunt for The condensate formed from the water vapor contained therein can be discharged intermediately. child This reduces the thermal resistance of the condensate film that tends to form on the inner surface of the first slit-like passage. The intensity of heat exchange is improved because of the reduced heat exchange.

Additionally, the provision of intermediate headers allows different heat transfer sections to have different thermal properties and Improves overall heat exchange efficiency when using a second fluid medium with different physical properties can be set.

This advantage is that using an intermediate header allows the second slot in different heat transfer sections to This is achieved by allowing the net-like channels to be structurally different. Therefore , each heat transfer section! These passages in the can be configured depending on the thermal and physical properties of the fluid medium, thereby The most efficient heat transfer can be achieved in each heat transfer section. example media with different thermal and physical properties, such as cold compressed air, air and water. is used in the different heat transfer sections of the heat exchanger as the second fluid medium. If the plate heat exchanger of the present invention is used in a pre-plann sublant, several problems can be solved at once. can be solved. In other words, heat exchange can be performed more efficiently and pressure can be reduced. Heat reduction can be used and water consumption can be minimized.

In the plate heat exchanger of the present invention, projection onto a plane perpendicular to the first slit-like passage In the figure, the first slit-like passage in the first heat transfer section is connected to the adjacent heat transfer section. oriented at an angle to the first slint-like passageway of the thermal section; Therefore, the flow of the first fluid medium within the intermediate header can be strongly moved. .

This allows the first heat transfer secretin at the entrance to the first slit-like passageway to The temperature and velocity patterns of the flow of the fluid medium are further uniformed and The media streams are mixed so that the first fluid medium, such as compressed air, When conveyed from the thermal section to the second heat transfer section, the flow of compressed air is The first slint-like passage of the first heat transfer section is redirected in the header between The condensed falling water droplets can be easily separated from the compressed air inside.

The first transmission in a projection view on a plane perpendicular to the first slit-like passage; between the first slit-like passages of the heat section and the second heat transfer section; Preferably, the angle is about 90°. By setting this angle to approximately 90°, The flow of fluid media can be mixed most intensively.

As mentioned above, the plate heat exchanger according to the invention can be used with different fluid media. , high heat transfer efficiency can be obtained. Furthermore, the plate heat exchanger of the present invention is easy to manufacture. It is simple and can operate with confidence.

Brief description of the drawing These and other features of the invention will be explained in detail in conjunction with the accompanying drawings. It will become clearer from the following description of specific embodiments.

FIG. 1 is a front view showing the schematic configuration of the plate heat exchanger of the present invention, in which each heat transfer section is This is a cross-sectional view of a portion of the section.

FIG. 2 is a plan view of the plate heat exchanger of the present invention, with each heat transfer section partially cut away. It is shown face to face.

FIG. 3 is a sectional view taken along the line ■-■ in FIG. 1.

FIG. 4 is a sectional view taken along the line -IV in FIG. 1.

FIG. 5 is a sectional view taken along the line v-vvA in FIG. 1.

BEST MODE FOR CARRYING OUT THE INVENTION The plate heat exchanger according to the invention consists of three successively interconnected heat transfer sections 1 ．． 2.3 (Figures 1 and 2).

Each heat transfer section 1.2.3 has parallel heat transfer plates 4 (Fig. 2), 5 (first ), 6 (Fig. 2), and these heat transfer plates 4.5.6 are on the one hand first parallel slit-like channels 7 (Fig. 1), 8 (Fig. 2) for conveying a fluid medium of ), 9 (FIG. 1) and a second parallel slit shape iil for conveying another fluid medium. 10 (FIG. 1), 11 (FIG. 2), and '12 (FIG. 1).

In this case, the second parallel slit-like channels 10.11.12 are respectively are arranged substantially perpendicular to the net-shaped passages 7.8.9 and these N 1 passage 7.8.9 in heat exchange contact.

Section 1 includes a first slit-like passageway with a corrugated insert 13 (FIG. 3). 7 (Figs. 1 and 3) and a second slit with a wave insert) 14 (Fig. 2). It has a toe-shaped passage 10 (FIGS. 1 and 3). The second passage 10 is the first passage 7, in this case arranged perpendicularly to the first passage 7.

Section 1 1i! The i path 7 and the second path 10 are rectangles arranged parallel to each other. It is formed by a heat transfer plate 4 having a shape, and the heat transfer plate 4 has a first path 7 and the second passage 10 are brought into heat exchange contact. Heat transfer plates 4 in section 1 Spacers 15 (Fig. 3) and 16 (Fig. 2) are provided between the These spacers 15, 16 fluidly isolate the first passage 7 from the passage 10. , the corrugated insert 13, has the shape of a beam extending along the waves of ]4. Ru. The spacer 15 extends in the longitudinal direction of the insert 130 wave, while the spacer ser 16 extends in the longitudinal direction of the insert 140 waves. Spacer 15.16 The heat transfer plate 4, which together forms the passage 7.10, is covered by a rectangular sheet 17. Forms a stack with closed sides.

In the first slit-like channel 7 there is a first fluid medium (in this case coolable hot compressed air). A supply header 18 (FIGS. 1 and 2) is provided to supply A vibrator 19 for conveying this third fluid medium is connected to the supply header 18. tied together.

A second fluid medium (in this case cold cooling compressed air) is introduced into the second slit-like passage 10. To enable supply, a ladder 20 (Fig. 1) is provided to the supply. A vibe 21 for conveying this second fluid medium is connected to the supply header 20. Ru.

In order to be able to discharge the mth body medium from the second thrift-like passage 10, the discharge ( An outlet header 22 is provided for discharging the second fluid medium. A vibrator 23 is connected thereto. Heat transfer section 2 has corrugated inserts The first slit-like passage B8 (Fig. 2, Fig. 4) with a waveform a second thrift-like passageway 11 (Fig. 4) with an insert 25 (Fig. 1); have. The second passage B11 extends between the first passages 8, and in this case, It is arranged perpendicularly to the first passage 8.

The first passage 8 and the second passage 11 are rectangular heat transfer plates arranged parallel to each other. 5, and the heat transfer plate 5 connects the first passage 8 and the second passage B11. Heat exchange contact. A spacer 26 (Fig. 4) is provided between the heat transfer plates 5, 27 (FIG. 1) is provided to fluidly isolate the first passage 8 from the second passage 11. are doing. These spacers 26.27 correspond to the wave length of the corrugated inserts 24.25. It has the shape of a beam extending in the hand direction.

Spacer 26 extends along insert 240 waves, while spacer 27 extends along the insert 250 waves.

As shown in FIGS. 1 and 4, a passage 8.11 is formed with the spacer 26.27. The heat transfer plates 5 forming a closed stack with rectangular sheets 28 are doing.

Between the heat transfer sections 1 and 2, more specifically between the slit-like passages 7 and 8. In this case, an intermediate header 29 (FIGS. 1 and 2) is interposed. This intermediate header 29 are in communication with these heat transfer sections 1.2 and are connected to a first fluid medium (in this case (hot compressed air) is supplied from heat transfer section 1 to heat transfer section 2. ing.

A second fluid medium (atmosphere in this case) can be conveyed along the second slit-like passage 11. A supply header 30 (FIG. 2) is provided to ensure that the A vibrator 31 for conveying the second fluid medium is connected to 30.

In order to allow atmospheric air to be discharged from the second slint-like passage 11, a ladder 32 to the discharge is provided. (Fig. 2) is provided, and the discharge header 32 is used to transport this medium (atmosphere). A vibrator 33 is connected thereto. Section 2 is different from Section 1. As follows, that is, for the first slit-like passage 7.8 (Fig. In a projection onto a plane perpendicular to The angle (approximately 90° in this case) formed by sealing the first slit-like passageway 8 of section 2 angle). Similarly, the second slit of both sexes 1.2 The shaped passages 10 and 11 are also arranged at an angle to each other (in this case also at an angle of approximately 90°). This 90° angle provides the strongest flow of the first fluid medium within the ladder 29 towards the middle. This is preferable for mixing.

The heat transfer section 3 includes a first slit 7) with a corrugated insert 34 (FIG. 5). a second stage with a groove 9 (Figs. 1 and 5) and a corrugated insert 35 (Fig. 2); It has a lit-like passage 12.

The second slit-like passage 12 extends between the first slit-like passages 9. , it is arranged perpendicularly to the first thrift-like passage 9.

The first passage 9 and the second passage 12 are rectangular heat transfer plates 6 arranged parallel to each other. The heat transfer plate 6 connects the first passage 9 and the second passage 12 with heat. Exchange contacts. A spacer 36 (Fig. 5) is provided between the heat transfer plates 6, 37 (Fig. 2) is provided to fluidically isolate the first passage 9 from the second passage 12. It is cut off. Spacer 36 extends along insert 340 waves, while Spacers 37 extend along the corrugations of insert 35.

As shown in FIGS. 1 and 5, together with spacers 36.37 they form passages 9.12. The heat transfer plates 6 forming a closed stack with rectangular sheets 38 are doing.

between heat transfer sections 2 and 3, more particularly the first of these sections 2.3. An intermediate header 39 (Figures 1 and 2) is installed between the slit-shaped 11BS and 9. I'm being kicked. This intermediate ladder 39 communicates with these sections 2.3. , the first fluid medium (in this case hot compressed air) is transferred from section 2 to section 3. It is designed to be transported to

Section 3 1st slint i! Cooled compressed air can be discharged from li passage 9. A hood 40 is provided to the discharge, and the discharge header 40 has a pressure A vibrator 41 for discharging compressed air is connected.

A second fluid medium (cooling liquid in this case) can be supplied to the second slit-like passage 12. A supply header 42 (FIG. 1) is provided to allow the A vibrator 43 for conveying this medium (cooling liquid) is connected to.

In order to discharge the cooling liquid from the second slit-shaped passage B12, the discharge header 4 4 (Fig. 1), and the discharge ladder 44 is provided with a discharge ladder 44 for discharging this coolant. A second vibrator 45 is connected.

Section 5 section 3 is as follows for section 2, i.e. between the first slit In a projection onto a plane perpendicular to the shaped passage 8.9 (Figs. 4 and 5), the section The first slit-like passage 8 of section 2 is opposed to the first slit-like passage 9 of section 3. (in this case, an angle of about 909 degrees). similarly , the second slit-like passages 11.12 of both sexites 2.3 are also at an angle of approximately 90@ to each other. arranged in a uniform manner.

The plate heat exchanger according to the invention operates as follows. Compressor (show diagram) The fluid medium to be cooled, such as hot compressed air from It is conveyed to the supply header 18 and from there to the first slit-like passage 7 of the heat transfer section 1. distributed along. This hot air is conveyed along these first slit-like passages 7. While being heated, this hot air transfers some of its heat to another fluid medium (supplied from the vibrator 21). Reverse direction of cold compressed air conveyed through the heft 20 to the second slint-like passage 10 flow).

The hot compressed air is partially cooled in the first slit 7), while the cold pressure The compressed air is heated in the second slit-like passageway 10, adding capacity. heat When fresh compressed air flows along the first slit-like passage 7, condensation forms on the inner surface of the passage 7. A film of shrinkage is formed, the thickness of which gradually increases along the length of the passageway 7. I will do it.

The partially cooled hot compressed air flows from the first slit-like passage 7 to the intermediate header 29. The water flows into the water and is captured by condensed water. On the other hand, the heated compressed air is [Lit-shaped passage] flows into the outlet header 22 from the outlet header 22, and from the outlet header 22 the vibe 2 3 to a facility (not shown) that uses the compressed air.

In the intermediate header 29, hot compressed air is redirected in space and mixed intensively; Therefore, the speed and temperature of this hot compressed air remain constant while passing through the intermediate header 29. The layer is made uniform. At the same time, water droplets falling from compressed air are moderated by the action of inertia. It settles at the bottom of the header 29 from where it is drained by suitable known means (not shown). Served. From the intermediate header 29, compressed air flows into the first slit of the heat transfer section 2. It is distributed more evenly along the channel 8.

When the compressed air to be cooled flows along the first slint-like passage 8 of section 2 , the compressed air transfers some of its heat to a second fluid medium, such as the atmosphere. The vibrator 31 passes through the ladder 3° and is transported along the second slit-shaped passage 11. to be sent).

In the first slit-like passage 8, the hot compressed air is further cooled and The amount of moisture condensed on the surface increases. On the other hand, the atmosphere inside the second slit-like passage 11 is heated to a temperature required for heat utilization, for example.

The compressed air cooled in this manner is transferred from the first slit-like passage 8 to the intermediate ladder 3. 9. On the other hand, the heated atmosphere is discharged from the second slit-like passage 11. It flows into the ladder 32 and flows from the header 32 along the vibe 33 into the premises of the equipment (not shown). or other users of this utilized heat.

In the intermediate lid 39, as in the intermediate lid 29, the cooled The compressed air is intensively mixed to homogenize velocity and temperature patterns. So Afterwards, this compressed air is uniformly distributed along the first slit-like passage 9 of the heat transfer section 3. distributed to

The compressed air that has been cooled in this way is transferred to the first slit road 9 in section 3. flow along the line and transfer its heat to another cooler fluid medium (from the vibrator 43 to the supply header 4 2 and along the second slit-like passageway 12. ) to the desired level.

The cooled compressed air flows into the rudder 40 from the first slit-like passage 9 to the discharge; From the feeder 40, it is transported along the vibrator 41 to the subsequent compression process. , section 1 to the user. The falling water drops are inside the discharge header 40. and discharged via special means (not shown) suitable for discharge. cold The cooling liquid is conveyed from the second pickpocket road 12 to the discharge hood 44, and is then discharged from the cough hood 44. is discharged along the vibrator 45 or conveyed to the evaporator of the refrigerator. .

A viroft model of a plate heat exchanger according to the invention was manufactured and (Two-stage compressor blank with genuine D capacity and 0.8 MPa Extensive testing was carried out in connection with this. As a result of the test, the plate heat exchanger of the present invention , the consumption of cooling water can be reduced to 178 to 1/1o, and the combination It has been shown that up to 80% of the heat generated by the compression used to heat the It is proven.

Industrial applicability The present invention is suitable for installation in compressor plants where large amounts of water and electricity are consumed. The use of the present invention can reduce water consumption and , the heat of compression can be utilized more completely, and the power consumption for this purpose is small. Ru.

The present invention provides cooling and heating of process flows in air separation units. It can also be used in the chemical industry, refrigeration, gas production industry, mechanical engineering and transportation fields. can.

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Claims (2)

[Claims] 1. at least two heat transfer sections (1, 2); Each of the tubes (1, 2) is equipped with a parallel heat transfer plate (4, 5), which Between the heat transfer plates (4, 5) there is a first slit-like passages (7, 8) for a first fluid medium and said heat transfer plate (4); , 5) for the second fluid medium to be conveyed through the second slit-like channel (10, 1 1) is formed, and the first slit shape of the heat transfer section (1, 2) is formed. The passages (7, 8) are in continuous communication with each other and are connected to the supply header (18) and the discharge header (18). pipes (19) each supplying said first fluid medium via an output header (40); and a discharge pipe (41), while each of the heat transfer sections ( The second slit-like passage (10, 11) of 1, 2) is the first slit-like passage (7, 8) and from said first slit-like passageway (7, 8) a fluid supply headers (20, 30) and discharge headers (22, 32). ) and a vibrator (21, 31) respectively supplying said second fluid medium via In the plate heat exchanger communicating with the pipes (23, 33), between the first slit-like passages (7, 8) of each heat transfer section (1, 2) in contact with each other; The intermediate header (29) communicating with these first slit-like passages (7, 8) is said first slit-like passageway (7) of one heat transfer section (1); In a projection view onto a plane perpendicular to both first slit-like passages (7, 8), The angle formed by the first slit-like passageway (8) of the heat transfer section (2) on the other side is A plate-shaped heat exchanger characterized in that it is arranged without any. 2. In a projected view on a plane perpendicular to the first slit-like passages (7, 8) , both of the first heat transfer section (1) and the second heat transfer section (2). It is characterized in that the angle between the 1 slit-like passages (7, 8) is approximately 90°. A plate heat exchanger according to claim 1.