A gas storage dehumidification heat exchange integrated device compatible with non-powered and refrigeration dryers

Abstract

The application discloses a compatible gas storage dehumidification heat exchange integrated equipment for non-powered and refrigeration dryers, which comprises a pressure-bearing cylinder body; the inside of the pressure-bearing cylinder body is divided into three cavity bodies by a sealed partition plate, including a gas buffer cavity, a heat exchange cavity and an evaporation cavity; the pressure-bearing cylinder body is provided with a gas inlet communicating with the gas buffer cavity and a gas outlet communicating with the heat exchange cavity; the bottom of the gas buffer cavity and the bottom of the heat exchange cavity are communicated and provided with a first hydrophobic port; the heat exchange cavity is internally provided with a heat exchanger; the bottom of the heat exchange cavity is provided with a primary defoamer; the evaporation cavity is internally provided with an evaporator; the bottom of the evaporation cavity is provided with a secondary defoamer; the lower portion of the secondary defoamer is provided with a second hydrophobic port. Compared with the prior art, the application has the advantages that a compatible gas storage dehumidification heat exchange integrated equipment for non-powered and refrigeration dryers is provided, which integrates gas storage, two-stage dehumidification and pre-cooling evaporation.

Description

Technical Field

[0001] This invention relates to the technical field of air compressor post-treatment purification equipment, specifically to an integrated air storage, dehumidification, and heat exchange device compatible with both non-powered and refrigerated dryers. Background Technology

[0002] The existing standard post-treatment process for industrial compressed air is as follows: air compressor → wet air receiver → Q-grade precision filter → split-type refrigerated dryer → P / S-grade precision filter. The entire system consists of multiple independent devices connected in series, with an inlet air temperature of 40-50℃, requiring a stable atmospheric dew point of 5-10℃ for the final supplied air. This traditional process has the following drawbacks:

[0003] 1. Multiple independent devices are connected in series, resulting in long pipelines, high overall pressure drop, and huge energy consumption. The devices are connected by flanges, elbows, and reducers, resulting in numerous pipeline nodes and a total system pressure loss of 0.003-0.005MPa. The insulation of the segmented pipelines is poor, and a large amount of cold air is lost during the process of transporting the low-temperature air from the evaporator to the precooler, which greatly reduces the heat exchange efficiency.

[0004] Second, the independent air storage tank, Q filter, and refrigerated dryer occupy the same space, resulting in low utilization of factory space. The four pressure vessels are arranged in parallel series, with an extremely long axial length, making it impossible to place them in the small machine room of a medium-sized air compressor station.

[0005] 3. The multi-stage, dispersed water distribution system results in mixed flow of high and low temperature water, leading to large fluctuations in the outlet dew point and a tendency for water to be carried over. The storage tank relies solely on gravity settling to separate large liquid water particles, while all fine water mist enters the downstream filter. The high-temperature condensate from the pre-cooling section is carried by the airflow into the low-temperature evaporator, where it undergoes secondary vaporization upon encountering the low-temperature chamber, generating additional water vapor. The entire system has only one main drainage point in the refrigerated dryer, and backflow of accumulated water causes secondary humidification of the compressed air.

[0006] Fourth, the maintenance and repair procedures are cumbersome, and a single equipment failure can cause the entire line to shut down. The air tank draining, Q filter element replacement, and refrigerated dryer cleaning are three separate maintenance procedures, requiring multiple shutdowns for disassembly and reassembly. After the refrigerated dryer is repaired, all the air needs to be recooled from room temperature to a stable dew point, interrupting the production line. Summary of the Invention

[0007] The technical problem to be solved by the present invention is to overcome the above-mentioned technical defects and provide an integrated gas storage, dehumidification and heat exchange device that integrates gas storage, two-stage dehumidification and pre-cooling evaporation and is compatible with both non-powered and refrigerated dryers.

[0008] To solve the above-mentioned technical problems, the technical solution provided by the present invention is: an integrated gas storage, dehumidification, and heat exchange device compatible with both non-powered and refrigerated dryers, including a pressure-bearing cylinder;

[0009] The interior of the pressure-bearing cylinder is divided into three cavities by a sealed partition, including a gas buffer cavity, a heat exchange cavity, and an evaporation cavity. The pressure-bearing cylinder is provided with an air inlet communicating with the gas buffer cavity and an air outlet communicating with the heat exchange cavity.

[0010] The bottom of the gas buffer chamber is connected to the bottom of the heat exchange chamber and is provided with a first condensate drain. The heat exchange chamber contains a heat exchanger and a first-stage demister is provided at the bottom of the heat exchange chamber.

[0011] The evaporation chamber contains an evaporator, and a secondary demister is provided at the bottom of the evaporation chamber. A second condensate drain is provided below the secondary demister.

[0012] Preferably, the right end of the pressure-bearing cylinder is provided with a detachable sealing head.

[0013] Preferably, there are two sealing partitions, and each of the two sealing partitions is provided with a one-way airflow channel. The one-way airflow channel includes an air inlet channel located at the lower part of the sealing partition and a return channel located at the upper part of the sealing partition.

[0014] Preferably, the heat exchanger is a counter-current heat exchange structure, in which the high-temperature intake air in the heat exchange chamber exchanges heat with the low-temperature air returning from the evaporation chamber in a counter-current manner;

[0015] The primary demister intercepts fine water mist and oil droplets.

[0016] Preferably, the evaporator circulates refrigerant to cool the pre-cooled air to a normal dew point of 5-10°C.

[0017] The secondary demister captures low-temperature micro water mist.

[0018] Preferably, the first drain outlet and the second drain outlet are set independently to discharge condensate at different temperature ranges.

[0019] Preferably, the air inlet is directly connected to the air compressor exhaust port, and the air outlet is connected to a rear-end P-level and S-level precision filter.

[0020] Preferably, the outer side of the pressure-bearing cylinder is also provided with an integral heat insulation structure.

[0021] Preferably, the air intake channel forms an air intake channel structure, and the gas flow direction of the air intake channel structure includes sequentially passing through the gas buffer chamber, the air intake channel below the first sealing partition, the heat exchange chamber, the air intake channel below the second sealing partition, and then to the evaporation chamber.

[0022] The reflux channel forms an outlet airflow channel structure. The dry air in the evaporation chamber returns to the heat exchange chamber through the reflux channel at the top of the second sealing partition plate. After counter-current heat exchange with the high-temperature intake air, it is discharged from the outlet.

[0023] Another aspect of the present invention discloses a method of using a gas storage dehumidification heat exchange device compatible with both non-powered and refrigerated dryers, comprising the following steps:

[0024] S1: Compressed air enters the gas buffer chamber through the air inlet for pressure stabilization and buffering, and undergoes gravity water separation. The condensate is discharged from the first drain port.

[0025] S2: The airflow enters the heat exchange chamber through the sealed partition plate, and is pre-cooled by counter-current heat exchange with the return low-temperature air through the heat exchanger and condensate is precipitated. After the water is removed by the first-stage demister, it is discharged from the first drain port.

[0026] S3: After pre-cooling, the airflow enters the evaporation chamber through the sealed partition plate, is deeply cooled and dehumidified by the evaporator, and is discharged from the second condensate outlet after water removal by the secondary demister.

[0027] S4: Dry, low-temperature air flows back to the heat exchange chamber through a sealed partition to be heated, and then outputs from the outlet.

[0028] The advantages of this invention compared to the prior art are:

[0029] 1. One machine replaces three independent machines, simplifying the entire post-processing process. This machine integrates five functions: air storage, gravity primary water separation, equivalent Q-level oil-water separation, pre-cooling and reheating, and low-temperature evaporation and drying. It directly eliminates the traditional wet air storage tank, Q-level filter, and split refrigerated dryer. The air compressor outlet is directly connected to this machine, and only P and S terminal fine filters are retained at the back end.

[0030] 2. By eliminating numerous intermediate connecting pipes, the overall system pressure drop is significantly reduced. All flanges, elbows, and reducers in the equipment room are eliminated, eliminating a large amount of local resistance and reducing the overall system pressure loss by more than 60%. Hot and cold airflows exchange heat in a close-range counter-current manner within the same cylinder, eliminating heat loss through external piping and improving heat recovery efficiency by 15%-25%.

[0031] 3. The three-section cavity has two independent water separation stages to avoid secondary vaporization of condensate, ensuring a stable dew point. The gas buffer cavity separates large water droplets by gravity, the heat exchange cavity has a first-stage demister to intercept fine oil mist and water mist, and the evaporation cavity has a second-stage demister to capture low-temperature micro-droplets. The accumulated water is discharged in separate zones, so high-temperature water will not enter the low-temperature evaporation cavity and re-vaporize. The outlet gas maintains a stable dew point of 5-10℃ at normal pressure.

[0032] 4. The whole machine is highly integrated, reducing the floor space by more than 60%. It has only a single pressure-bearing cylinder, end caps, and two sets of main inlet and outlet flanges. There is no need to manufacture separate air storage tanks, filter tanks, and refrigerated dryer shells. Only one set of overall insulation structure is used to adapt to wide temperature difference conditions, greatly reducing consumables. There is no need to purchase and replace Q-grade filter elements separately or regularly.

[0033] 5. The workload of installation, inspection and maintenance is greatly simplified. Only two pipelines need to be connected on site, and the installation manpower is halved; the shell has a detachable end cap on one side, and all heat exchangers and two-stage demisters can be extracted at the same time; the drain ports of the three-section chamber can be independently flushed and drained online; when the equipment is restarted, only the air in a single shell needs to be cooled, shortening the production line downtime.

[0034] 6. No additional power structure, compatible with non-powered air compressors. The whole machine relies solely on the air compressor's own air supply pressure to drive airflow circulation. There are no auxiliary power components such as fans or booster pumps inside the cylinder. For non-powered dryers with low air supply pressure and large air source fluctuations, the air storage buffer chamber can stably buffer pressure fluctuations, making it suitable for a wider range of scenarios. Attached Figure Description

[0035] Figure 1 This is a structural diagram of an integrated gas storage, dehumidification, and heat exchange device that is compatible with both non-powered and refrigerated dryers.

[0036] Figure 2 This is a cross-sectional structural diagram of an integrated gas storage, dehumidification, and heat exchange device compatible with both non-powered and refrigerated dryers.

[0037] Figure 3 This is a structural schematic diagram of a second-view cross-section of an integrated gas storage, dehumidification, and heat exchange device that is compatible with both non-powered and refrigerated dryers.

[0038] Figure 4 This is a schematic diagram of the internal gas flow of an integrated gas storage, dehumidification, and heat exchange device that is compatible with both non-powered and refrigerated dryers.

[0039] As shown in the figure: 1. Pressure-bearing cylinder, 2. Gas buffer chamber, 3. Heat exchange chamber, 4. Evaporation chamber, 5. Air inlet, 6. Air outlet, 7. First drain port, 8. Heat exchanger, 9. Primary demister, 10. Evaporator, 11. Secondary demister, 12. Second drain port, 13. Removable sealing head, 14. Sealing partition plate, 15. P-grade precision filter, 16. S-grade precision filter. Detailed Implementation

[0040] The present invention will now be described in further detail with reference to the accompanying drawings.

[0041] Combined with appendix Figure 1-4 As shown, an integrated gas storage, dehumidification, and heat exchange device compatible with both non-powered and refrigerated dryers includes a pressure-bearing cylinder 1;

[0042] The interior of the pressure-bearing cylinder 1 is divided into three cavities by a sealing partition 14, including a gas buffer cavity 2, a heat exchange cavity 3 and an evaporation cavity 4. The pressure-bearing cylinder 1 is provided with an air inlet 5 communicating with the gas buffer cavity 2 and an air outlet 6 communicating with the heat exchange cavity 3.

[0043] The bottom of the gas buffer chamber 2 is connected to the bottom of the heat exchange chamber 3, and a first drain outlet 7 is provided. The heat exchange chamber 3 is equipped with a heat exchanger 8, and a first-stage demister 9 is provided at the bottom of the heat exchange chamber 3.

[0044] The evaporation chamber 4 is equipped with an evaporator 10, and a secondary demister 11 is provided at the bottom of the evaporation chamber 4. A second condensate drain 12 is provided below the secondary demister 11.

[0045] When in use, the right end of the pressure cylinder 1 is provided with a detachable sealing head 13, which is convenient for disassembly and internal maintenance. There are two sealing partitions 14, and each of the two sealing partitions 14 is provided with a one-way airflow channel. The one-way airflow channel includes an air inlet channel located at the lower part of the sealing partition 14 and a return channel located at the upper part of the sealing partition 14.

[0046] The air intake channel forms an air intake channel structure, and the gas flow direction of the air intake channel structure includes passing through the gas buffer chamber 2, the air intake channel under the first sealing partition 14, the heat exchange chamber 3, the air intake channel under the second sealing partition 14, and then to the evaporation chamber 4 in sequence.

[0047] The reflux channel forms an outlet airflow channel structure. The dry air in the evaporation chamber 4 returns to the heat exchange chamber 3 through the reflux channel on the upper part of the second sealing partition 14. After counter-current heat exchange with the high-temperature inlet air, it is discharged from the outlet 6.

[0048] In one embodiment:

[0049] Heat exchanger 8 is a counter-current heat exchange structure, in which high-temperature intake air in heat exchange chamber 3 exchanges heat with low-temperature air returning from evaporation chamber 4 in a counter-current manner;

[0050] The primary demister 9 intercepts fine water mist and oil droplets;

[0051] Evaporator 10 circulates refrigerant, cooling the pre-cooled air to 5-10℃ at atmospheric pressure dew point;

[0052] The secondary demister 11 captures low-temperature micro water mist;

[0053] The first drain outlet 7 and the second drain outlet 12 are set independently to discharge condensate at different temperature ranges.

[0054] During assembly and use, the air inlet 5 is directly connected to the air compressor exhaust port, and the air outlet 6 is connected to the rear-end P-level precision filter 15 and S-level precision filter 16.

[0055] In one embodiment:

[0056] The outer side of the pressure cylinder 1 is also equipped with an overall heat insulation structure.

[0057] In specific implementation of the present invention,

[0058] An integrated refrigerated dryer that combines gas storage, two-stage dehumidification, and pre-cooling evaporation has a main body consisting of a single pressure-bearing cylinder 1. The interior of the cylinder is divided into three chambers along the airflow direction by a sealed partition 14: a left gas buffer chamber 2, a middle heat exchange chamber 3, and a right evaporation chamber 4.

[0059] The air inlet 5 on the left end of the cylinder is directly connected to the air compressor exhaust port, eliminating the need for an intermediate air tank and a pre-Q filter; the air outlet 6 on the right end is connected to the rear-end P-level precision filter 15 and S-level precision filter 16.

[0060] Gas buffer chamber 2: The volume meets the pressure stabilization and buffering requirements of the air compressor. Large particles of condensate are collected by gravity settling and discharged through the first drain port 7, replacing the traditional wet gas storage tank's pressure stabilization and preliminary dehumidification functions.

[0061] Heat exchange chamber 3: Internal heat exchanger 8, gas buffer chamber 2 outflows 40-50℃ humid hot air and evaporator 10 return 5-10℃ low temperature air for counter-current heat exchange, the inlet air is pre-cooled to 20-28℃; a first-stage demister 9 is set at the bottom of the chamber, which can intercept fine water mist and oil droplets, and the water separation capacity is equivalent to an independent Q-stage filter, eliminating the need for an external Q filter tank; medium temperature condensate is discharged from the first drain port 7 at the bottom of the chamber.

[0062] Evaporation chamber 4: An internal evaporator 10 circulates refrigerant, cooling pre-cooled air to a normal dew point of 5-10℃, completely condensing any residual water vapor in the air. A secondary demister 11 at the bottom of the chamber captures low-temperature micro-water mist, and a second drain port 12 discharges low-temperature condensate. A fully removable sealing head 13 is installed at the right end of the cylinder; after disassembly, the heat exchanger 8, evaporator 10, and two-stage demisters can be simultaneously extracted for convenient cleaning and maintenance. Two sealed partition plates 14 provide unidirectional airflow channels, forcing air to flow unidirectionally from the gas buffer chamber 2 to the heat exchange chamber 3 and then to the evaporation chamber 4. Dry, cold air flows back to the heat exchange chamber 3 along the upper channel of the sealed partition plate 14, heating to 15-25℃ before being discharged, preventing short-circuiting of dry / wet or hot / cold airflows. The drain ports in the gas buffer chamber 2, heat exchange chamber 3, and evaporation chamber 4 are completely independent, discharging condensate at different temperature ranges in separate areas, preventing high-temperature water from flowing into the low-temperature chamber and undergoing secondary vaporization.

[0063] Complete process flow of the whole machine: saturated humid and hot compressed air → pressure stabilization and gravity water separation in gas buffer chamber 2 → water mist capture by primary demister 9 → pre-cooling by heat exchanger 8 in heat exchange chamber 3 → precipitation of a large amount of liquid water (condensate is discharged from the first drain port 7) → after pre-cooling, the air passes through the sealed partition 14 into the evaporation chamber 4, and is deeply dried to 5-10℃ by the evaporator 10 → residual moisture in the air condenses → fine water mist is captured by secondary demister 11 (residual moisture and condensate are discharged from the second drain port 12) → low-temperature dry air flows back through the sealed partition 14 to the heat exchange chamber 3 and is heated to 15-25℃ → counter-current heat exchange with the inlet high-temperature humid and hot air to prevent condensation on the outer wall of the pipe → dry air is output from the outlet 6 and sent to the P-level precision filter 15 and S-level precision filter 16 for production use.

[0064] The contents not described in detail in this specification are existing technologies known to those skilled in the art.

[0065] The working principle of this invention is as follows:

[0066] It should be noted that similar labels and letters in the following figures indicate similar items. Therefore, once an item is defined in one figure, it does not need to be further defined and explained in subsequent figures.

[0067] The present invention and its embodiments have been described above. This description is not restrictive, and the accompanying drawings are only one embodiment of the present invention; the actual structure is not limited thereto. In conclusion, if those skilled in the art are inspired by this description and design similar structures and embodiments without departing from the spirit of the invention, such designs should fall within the protection scope of the present invention.

Claims

1. An integrated gas storage, dehumidification, and heat exchange device compatible with both non-powered and refrigerated dryers, characterized in that: Including the pressure-bearing cylinder (1); The interior of the pressure-bearing cylinder (1) is divided into three cavities by a sealing partition (14), including a gas buffer cavity (2), a heat exchange cavity (3) and an evaporation cavity (4). The pressure-bearing cylinder (1) is provided with an air inlet (5) communicating with the gas buffer cavity (2) and an air outlet (6) communicating with the heat exchange cavity (3). The bottom of the gas buffer chamber (2) is connected to the bottom of the heat exchange chamber (3), and a first drain port (7) is provided. The heat exchange chamber (3) is equipped with a heat exchanger (8), and a first-stage demister (9) is provided at the bottom of the heat exchange chamber (3). The evaporation chamber (4) has an evaporator (10) inside, and a secondary demister (11) is provided at the bottom of the evaporation chamber (4). A second drain outlet (12) is provided below the secondary demister (11).

2. The integrated gas storage, dehumidification, and heat exchange equipment compatible with both non-powered and refrigerated dryers according to claim 1, characterized in that: The right end of the pressure-bearing cylinder (1) is provided with a detachable sealing head (13).

3. The integrated gas storage, dehumidification, and heat exchange equipment compatible with both non-powered and refrigerated dryers according to claim 1, characterized in that: The sealing partition (14) consists of two sections, each of which is provided with a one-way airflow channel. The one-way airflow channel includes an air inlet channel located at the lower part of the sealing partition (14) and a return channel located at the upper part of the sealing partition (14).

4. The integrated gas storage, dehumidification, and heat exchange equipment compatible with both non-powered and refrigerated dryers according to claim 1, characterized in that: The heat exchanger (8) is a counter-current heat exchange structure, in which the high-temperature air in the heat exchange chamber (3) and the low-temperature air returning from the evaporation chamber (4) exchange heat in a counter-current manner. The primary demister (9) intercepts fine water mist and oil droplets.

5. The integrated gas storage, dehumidification, and heat exchange equipment compatible with both non-powered and refrigerated dryers according to claim 4, characterized in that: The evaporator (10) circulates refrigerant to cool the pre-cooled air to a normal dew point of 5-10°C. The secondary demister (11) captures low-temperature micro water mist.

6. The integrated gas storage, dehumidification, and heat exchange equipment compatible with both non-powered and refrigerated dryers according to claim 1, characterized in that: The first drain outlet (7) and the second drain outlet (12) are set independently to discharge condensate at different temperature ranges respectively.

7. The integrated gas storage, dehumidification, and heat exchange equipment compatible with both non-powered and refrigerated dryers according to claim 1, characterized in that: The air inlet (5) is directly connected to the air compressor exhaust port, and the air outlet (6) is connected to the rear-end P-level precision filter (15) and S-level precision filter (16).

8. The integrated gas storage, dehumidification, and heat exchange equipment compatible with both non-powered and refrigerated dryers according to claim 1, characterized in that: The pressure-bearing cylinder (1) is also provided with an overall heat insulation structure on its outer side.

9. The integrated gas storage, dehumidification, and heat exchange equipment compatible with both non-powered and refrigerated dryers according to claim 3, characterized in that: The air intake channel forms an air intake channel structure. The gas flow direction of the air intake channel structure includes passing through the gas buffer chamber (2), the air intake channel under the first sealing partition (14), the heat exchange chamber (3), and the air intake channel under the second sealing partition (14) to the evaporation chamber (4) in sequence. The reflux channel forms an outlet airflow channel structure. The dry air in the evaporation chamber (4) returns to the heat exchange chamber (3) through the reflux channel at the top of the second sealing partition (14), and is discharged from the outlet (6) after countercurrent heat exchange with the high-temperature inlet air.

10. A method of using a gas storage dehumidification and heat exchange device compatible with both non-powered and refrigerated dryers, wherein the device is used as described in any one of claims 1-9, characterized in that: Includes the following steps: S1: Compressed air enters the gas buffer chamber (2) through the air inlet (5) to stabilize the pressure and buffer the air, and then performs gravity water separation. The condensate is discharged from the first drain port (7). S2: The airflow enters the heat exchange chamber (3) through the sealed partition (14), and is pre-cooled by counter-current heat exchange with the return low temperature air through the heat exchanger (8) and condensate is precipitated. After the water is removed by the first-stage demister (9), it is discharged from the first drain port (7). S3: After pre-cooling, the airflow enters the evaporation chamber (4) through the sealed partition (14), is deeply cooled and dehumidified by the evaporator (10), and is discharged through the second drain port (12) after water removal by the secondary demister (11). S4: Dry, low-temperature air flows back to the heat exchange chamber (3) through the sealed partition (14) and is heated before being output from the outlet (6).

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