JP4406787B2 - Warm and dry air blowing type dryer using piston type air compressor - Google Patents

Description

The present invention relates to a hot dry air blowing type drying apparatus using a piston type air compressor (air compression structure) , and has the following characteristics. In other words, the piston type air compressor has the feature that the mechanism that makes the mechanism compact can be obtained by eliminating the part where the first stage compression part is connected by piping in the two stage compression mechanism, and the ability to compress the pipe part is not possible. It has the feature that the piping part is eliminated and the capacity is improved, and the fixed side without the valve can make the air intake and exhaust by the reciprocating motion of the second piston member, and the cooling that suppresses heat generation It has characteristics that are effective.

  At present, various types of air compressors (air compression structures) have been proposed. Among them, there are methods in which a piston (reciprocal) type and a screw type are mainly used, but the basic performance has advantages and disadvantages, and a breakthrough in performance is required. The existing piston type air compressor is a single piston type, so the maximum load is large and air pulsation becomes intense, and the vibration and noise are large due to poor rotation balance. Also, the higher the pressure, the greater the heat generation. As a result, it can be said that the current state of the conventional piston type is that a low-speed operation with a large intake volume is forced. In addition, since the screw type air compressor is manufactured using high precision and advanced technology, maintenance is important from the precision of the mechanism, and there is a problem that running cost is high. Furthermore, although the rotation balance is good, the current situation is that it is not suitable for high-pressure production because the compression volume is small in one-stage compression. In summary:

  In principle and structure, the piston type cannot be operated at high speed. The piston type has a structure that cannot be balanced structurally, and has a large noise as well as vibration. In the piston type, since air pulsation is large, it is necessary to enlarge the storage tank to stabilize the air. Both the screw type and piston type generate large amounts of heat and often require cooling.

  Therefore, from the drive transmission structure of the rotating shaft patented by the present applicant in 1996 (see Patent Documents 1 and 2), pay attention to the air pressure that works in the same way as the repulsive force of the magnet. A new theory has been developed in which two pistons are compressed in two stages with different crank diameters.

1. A system in which both cylinder members are shared and compressed in two stages with a difference in crank diameter (effective for high pressure production).
2. The piston has a valve and compresses in two stages according to the difference in crank diameter (suppresses heat generation and is effective for high-speed rotation).
3. The piston has a valve and compresses in two stages with different crank diameters (effective for power-saving and low-cost manufacturing).

  If these techniques 1 to 3 are utilized, various structures such as high pressure, compact, low heat, low cost, and high speed rotation can be achieved.

On the other hand, the present applicant has developed a piston-type air compression device and the like (double piston-type air compressor) having more excellent air compression capability (see Patent Document 2). However, in this piston type air compressor, there is a problem in that the capacity is reduced because the air in the pipe connected between the cylinder members by the pipe cannot be compressed between the cylinder members. In addition, there is a difficulty in making the structure compact.
Japanese Patent No. 2073648 PCT / JP02 / 09777 (Pamphlet)

The present invention has been made to solve the above-described problems, and the object of the present invention is to provide hot and dry air blowing type drying using a high performance and compact piston type air compressor (air compression structure ). To provide an apparatus.

(Claim 1)
In order to achieve such an object, a warm dry air blowing type drying apparatus using a piston type air compressor according to claim 1 is characterized in that , as the piston type air compressor, the first piston member is placed on the cylinder head side, The piston members are opposed to each other in a straight line in the same cylinder member on the crank side, and the piston shaft member of the first piston member is penetrated through the second piston member so that both piston shaft members are concentrated on one side, In a structure that can compress air in two stages by reciprocating in the same direction with a difference in crank diameter,
The cylinder lid on the cylinder head side includes an intake valve, the cylinder member includes an exhaust connection part including an exhaust valve, and the first piston member has an intake valve, and the first piston When the member is provided with the intake valve and reciprocates in cooperation with the second piston member, the gap air sandwiched between the cylinder head side cylinder lid provided with the intake valve and the first piston member becomes the first piston member. The first piston member and the second piston member, which reciprocate in association with each other through the intake valve, are compressed in one step and are continuously reciprocated by these two piston members. The compressed air is compressed in two stages and exhausted from the exhaust connection parts of the cylinder member, thereby eliminating the pipe used for the first compression of the cylinder member. Furthermore, between the second piston member and the crank side cylinder lid, there is provided a cylindrical space in which external air can be sucked and discharged by reciprocating movement of the second piston member, and its air supply / exhaust hole. In addition, the cylinder member can be positively cooled by extending the crank side of the second piston member in a skirt shape.
The piston type air compressor used in the warm dry air blowing type drying apparatus according to claim 1 will be described with reference numerals used in FIG. 1. A crank mechanism 0014 having different crank angles and crank radii is provided with a crank mechanism. It is composed of connecting rods 0011, 0012, 0013 and crankshafts 0080, 0090, 0010, which are coupled to each other so as to be able to perform rotational movement and piston reciprocation.
Further, each crankshaft has a valve 0040 inserted into a first piston member 0030 and a second piston member 0050 coupled thereto.
The piston portion was housed in a cylinder lid 0010 having an intake valve 0020, a cylinder member 0060 with an exhaust valve, and a cylinder lid 0070 with a shaft hole / cooling hole.
The gist of the invention is that an exhaust connection component 0018 having an exhaust valve 0017 is attached to the cylinder member 0060.
The Yutakainui air blowing type drying apparatus of the present invention, a piston type air compressor described above, the dehumidifying unit dehumidifies the compressed air from the piston type air compressors, piston type air compressors by dehumidified air by dehumidifying means Air cooling means for cooling the constituting cylinder member, and drying means for blowing the garbage used for cooling by the air cooling means by spraying garbage, laundry or other moisture, and drying.
The temperature dry air blowing type drying apparatus according to claim 1, wherein having such a configuration, a dehumidifier, compressed air from the piston type air compressor is dehumidified by cooling means, the cylinder member constituting such a piston type air compressor cooling Then, by the drying means, the gas subjected to cooling by the air cooling means, that is, the warmed gas is sprayed on the moisture.
(Claim 2 )
The hot and dry air blowing type drying apparatus according to claim 2 is the hot and dry air blowing type drying apparatus according to claim 1, wherein the cooling means is disposed outside the coaxial member of the cylinder member constituting the piston type air compressor. A cylinder member and a guide air supply pipe for supplying the gas dried by the drying means to the gap between the outer cylinder member and the cylinder member are provided.
According to the warm-dry air blowing type drying apparatus according to claim 2 having such a configuration, the air-drying drying apparatus according to claim 1 operates in the same manner as the warm-drying air blowing type drying apparatus according to claim 1 , and is dried by the drying means by the guide air supply pipe. When the gas is supplied to the gap between the outer cylinder member and the cylinder member, the supplied gas comes into contact with the outer surface of the side wall of the cylinder member, and the cylinder member is cooled.
(Claim 3 )
According to a third aspect of the present invention, there is provided the warm dry air blowing type drying apparatus according to the first or second aspect , wherein the drying means blows gas from below the moisture.
According to the warm dry air blowing type drying apparatus according to claim 3 having such a configuration, it operates in the same manner as the warm dry air drying apparatus according to claim 1 or 2 , and further from the lower side of the moisture by the drying means. Moisture is agitated because the gas is blown.

(Claim 1)
According to the piston type air compressor (air compression structure) used in the hot and dry air blowing type drying apparatus according to claim 1, the reciprocating mechanism of the piston shaft member is concentrated on one side and sucked into the cylinder A of the volume. By inserting an intake valve into the first piston member, the conventional pipe connection is eliminated, and two-stage compression is performed with a difference between the crank radius of 13.5 mm and 10'5 mm. The volume cylinder C can be used for cooling. In addition, the cylinder A having a stroke of 27 mm has a load of a radius of 10.5 mm and is efficient for the first compression. If this mechanism is combined into a multi-cylinder system, the overall balance will be achieved, and this can be realized with a highly efficient, high-speed rotation and compact mechanism.
According to the warm dry air blowing type drying apparatus of claim 1, since the cylinder member is cooled by the compressed air dehumidified by the dehumidifying means, it is possible to prevent the cylinder member from being damaged. is there. In addition, since the gas supplied for cooling by the air cooling means is blown onto the moisture, there is an effect that the gas supplied for cooling and heated can be used effectively. Furthermore, since the gas blown to the moisture is a gas compressed by the piston type air compressor, it is possible to stir the moisture and dry the whole.
(Claim 2 )
According to the hot and dry air blowing type drying apparatus of claim 2 , in addition to the effect exhibited by the hot and dry air blowing type drying apparatus of claim 1 , the cooling means is constituted by a guide air supply pipe and an outer cylinder member. Since the gas dried by the drying means is supplied to the gap between the outer cylinder member and the cylinder member by the guide air supply pipe, the cooling means can be realized with a simple mechanism. There is an effect.
(Claim 3 )
According to the warm dry air blowing type drying apparatus according to claim 3, wherein, in addition to the effects of temperature dry air blowing type drying apparatus according to claim 1 or 2, the drying means, gas blown from the lower side of the moisture was Therefore, it is possible to stir the moisture substance and to dry the entire moisture substance.

Although the example (Example) of embodiment of the air compression structure of the piston type air compressor used for the hot-dry air blowing type drying apparatus concerning this invention is demonstrated , this is a representative example. The present invention is not limited to the following examples unless the gist thereof is exceeded. For example, the gas to be compressed is not limited to air as well as the crank length, the crank radius, the size of the crank mounting angle, and the like.

(First embodiment)
First, it is assumed that the crank mechanism 0014 shown in FIG. 1 is 180 degrees forward and 360 degrees backward on the counterclockwise horizontal line with respect to the crank rotation center. The crank mechanism 0013 has a radius of 10.5 mm-360 degrees, and the crank mechanisms 0011, 0012 have a radius of 13.5 mm-365 degrees.

  The crank mechanism 0014 is connected to the connecting rods 0011 and 0012, the piston shaft members 0090 and 0010, and the first piston member 0030, and the connecting rod 0013 is connected to the piston shaft member 0010 and the second piston member 0050, and is housed in the cylinder member. A structure that can reciprocate against rotational movement.

  A cylinder lid 0010 having an intake valve 0020, a cylinder member 0060 having an exhaust valve 0017, an exhaust connection part 0018 having an exhaust valve 0017, and a cylinder lid 0070 having a shaft hole cooling hole are used. A two-stage compression mechanism containing a piston member and a second piston member.

  When the crank mechanism 0014 rotates counterclockwise, the first piston member 0030 and the second piston member 0050 reciprocate within the cylinder member by the crank radius.

  At this time, cylinders A and B having a volume sandwiched between the first piston member 0030 and the second piston member 0050 are formed within the cylinder member volume, and the air is compressed. Further, the cylinder C of the volume creates a compression stroke that is used for heat generation and cooling of the mechanism by circulating air.

  When the crank mechanism 0014 rotates 180 to 360 degrees counterclockwise, air is sucked from the intake valve 0020 into the cylinder A having a stroke of 27 mm and is confined by the accompanying rotation of the crank mechanism.

  At this time, the air in the cylinder B having the stroke of 6 mm, which has been compressed and confined, passes through the exhaust valve 0017 and is second compressed by the exhaust connection part 0018 and exhausted.

  Note that the air heated to high temperature due to the heat generation of the volume cylinder C is exhausted to the outside through an air supply / exhaust hole (not indicated).

  When the crank mechanism 0014 rotates by 0 to 180 degrees, the air in the cylinder A having a stroke of 27 mm that has been sucked in by the rotation of the crank mechanism passes through the intake valve 0040 inserted in the first piston member, and the stroke. First compressed into a cylinder B having a volume of 27 mm-21 mm = 6 mm and confined.

  At this time, the cylinder C of the volume receives fresh air from the outside and cools the cylinder member.

(Second embodiment)
Hereinafter, a modification of the above embodiment will be described with reference to FIGS. The second embodiment relates to a system in which a piston has a valve and compresses in two stages with different crank diameters, and is effective for power saving and low-cost manufacturing.

  As shown in each drawing, the piston type air compressor of the second embodiment is provided with one cylinder member and two pistons (intake valves are mounted on each piston). Here, the crank radius is 3 mm on one side and 12 mm on the other side, the intake stroke is 6 mm + 24 mm = 30 mm, and the compression stroke is 6 mm.

  As shown in FIG. 7, intake is completed within 30.5 mm between the pistons with the crank diameter of 3 mm being the most advanced / crank diameter of 12 mm being the last retreat. Simultaneously, the second compression stroke is completed with a crank diameter of 3 mm.

  As shown in FIG. 8, the crank diameter of 3 mm is 90 degrees backward and the crank diameter of 12 mm is 90 degrees forward, and the air of 30.5 mm between the pistons is pushed out before the valve of the first piston member is released and is compressed first. (Intake is increased by 25% to save power).

  As shown in FIG. 9, the crank diameter of 3 mm is 180 degrees backward and the crank diameter of 12 mm is 180 degrees forward, so that the air of 30.5 mm between the pistons is completely pushed out before the valve of the first piston member is released. Compression is complete. At this time, the air volume of the stroke 30 mm with the crank diameter 12 mm (stroke 24 mm) can be first compressed, and the efficiency is 25% better. Further, the second compression stroke and the intake stroke are performed simultaneously by the crank rotation in the future. (Heat generation is warmed by the outside air temperature on the inside and outside surfaces of the cylinder member, so that the rate of heat generation can be slowed and the saturation temperature can be reduced.)

  As shown in FIG. 10, the crank diameter of 3 mm is advanced 90 degrees and the crank diameter of 12 mm is retracted 90 degrees, so that the space between both pistons spreads and the outside air is released to 15.5 mm, and the piston B valve is released. At this time, when the crank diameter of the first piston member is 3 mm (stroke 6 mm), the second compression / exhaust stroke is performed simultaneously with the intake stroke. In addition, the completion of the intake and the completion of the second compression are performed sequentially, returning to FIG. This system has the feature that multiple cylinder members can be balanced and connected in parallel, providing compact, low cost and high performance.

  By configuring as described above, two-stage compression and residual pressure can be used mechanically, and high pressure production such as 50 Mpa can be easily performed.

  Also, in principle, a structure with a good rotation balance can be easily made, so that high-speed rotation is obtained, vibration is small, and noise is inevitably reduced.

  Since compression and intake are simultaneously performed by the same cylinder member and the heat radiation area of the cylinder member is large, heat generation is warmed and the temperature increase rate is reduced by about 30 to 50%. Conventionally, the structure in which two cylinder members are integrated into one can eliminate the connection piping between the cylinder members, and is approximately 50% compact and lightweight. If the intake stroke is for a low pressure, it can be up to 1.5 times the crank stroke distance, and power saving of 15 to 20% can be expected.

  The multi-cylinder member mechanism is easy and continuous exhaust is possible, reducing air pulsation and reducing tank capacity, leading to compactness and light weight.

  In summary, it is possible to design and manufacture a high-performance compact compressor that has low running costs and is easy to maintain, similar to the conventional piston type. From this, we believe that compressors that are widely used in various fields can be provided regardless of the usage environment.

The advantages of the above method are summarized below.
-Power saving: In the structural field, the intake volume can be increased by about 25% for 1.4 Mpa.
・ Small vibration: Since the rotation balance can be easily achieved, vibration is reduced. Noise: Since the package type with a tank can be made easily, the noise can be reduced to about 50 dB to 60 dB.・ Small size: Since the heat generation is low, high-speed continuous exhaust is possible with simple cooling. In other words, since air pulsation is reduced, the discharge amount can be secured even if the tank capacity is reduced, and compactness and light weight are possible.
-Power saving: Increasing the intake efficiency by about 25% increases the discharge amount and leads to power saving.
-Low price: The compact rate (about 50% compared to the previous model) can provide a comprehensively lower price than the conventional price.
-High pressure: A system that adds new air to the residual pressure and compresses it is easy to manufacture at high pressure.

  FIG. 11 is a diagram showing the principle of compression in the piston-type air compressor according to the second embodiment. As shown in FIG. 11, the amount corresponding to twice the reciprocating sliding distance (stroke) of both piston members. The intake gas can be sucked into the next stage (second stage) compression gap (first piston member (piston member on the far crankshaft side) and the bottom of the cylinder member on the far crankshaft side. It is possible to compress about twice as much by supplying air to the gap between the wall portion and further, by compressing by the reciprocating sliding motion of the first piston member, it can be highly compressed. There are benefits. During the second stage compression, the air is sucked into the first stage compression gap in the low pressure state, so that the compression is not hindered and the crankshaft is not forced. The reason why the compression ratio can be maximized as described above is that the first piston member and the second piston member (the piston member on the near crankshaft side) have different crank radii, and the first piston member and the second piston member. The phase difference of the reciprocating sliding motion differs between each piston member, and each piston member has an air supply valve (the cylinder member does not have to be provided with piping for supplying air to the compression gap in the next stage. It becomes possible to use a normal pipe member (without a special mechanism) for the member, and it becomes easy to dispose the cylinder member outside the cylinder member as will be described later, and it is easy to cool the cylinder member, etc. The piston shaft member for the first piston member can be passed through the second piston member (the crankshaft can be integrated into one). Both (when the crankshaft is combined into one, the mechanism is simplified and power saving is achieved), the intake valve and the exhaust valve are provided on the opposite bottom wall side), and the first piston member is the second one. It seems that the sliding distance is larger than that of the piston member. Of course, all these reasons have not been met, but even if all the reasons are not necessarily met, it can be easily guessed that the compression ratio of the piston type air compressor according to the present invention is sufficiently high. I think that the.

  FIGS. 11 and 12 are diagrams showing a first application example of the (first and second) embodiments, and FIGS. 13 and 14 are diagrams showing a second application example.

  As shown in FIG. 11 and FIG. 12, according to the first application example, the cylinder member can be cooled to achieve high speed rotation, and the temperature difference can be achieved without providing a circulation mechanism (pump). Since the coolant (cooling water) circulates, the present invention can be easily applied to a portable device (for example, a tool such as a drill).

  Moreover, as shown in FIGS. 13 and 14, according to the second application example, the moisture is efficiently dried by blowing the moisture with compressed air (compressed air) that is dehumidified and warmed. be able to. In recent years, garbage processing devices have become widespread regardless of whether they are for home use or business use. However, it is considered that various problems of these processing devices (for example, bacteria type is odor) can be solved. Of course, the cylinder member can also be cooled, so that the speed of the piston member can be increased. In addition, what is shown in the figure is preferable because compressed air is blown from the lower side of the moisture substance, and it is not necessary to provide a separate stirring mechanism, but it is naturally not limited to this. Further, although not shown, the present invention can also be applied to a laundry dryer (of course, a stirring mechanism may be provided).

As mentioned above, although the piston type air compressor used for the warm dry air blowing type drying apparatus concerning the present invention was explained based on the example, of course, the example of the present invention is not limited to the above example, It goes without saying that various improvements and modifications can be made without departing from the spirit of the present invention. The technical scope of the present invention includes such improved modifications.

  The present invention has the features and advantages as described above, and it is considered that the advantages can be exhibited particularly in fields requiring high performance such as high pressure and high speed. Existing compressor application fields (machine tools, construction-related machines, medical instruments, food-related machines, textile-related machines, home appliances, etc.) Competition in these markets is intensifying.

  At the same time, there are high needs for high pressure, high speed, compactness, low vibration, low noise, energy saving, etc. By utilizing our developed compressor technology, the development and commercialization of small and high performance products will be facilitated. In other words, by incorporating this technology into the heart, it is possible to provide an application device that takes advantage of the features of the mechanism.

In addition, the piston type air compressor used for the warm dry air blowing type drying apparatus according to the present invention can be diverted to the following technique.

1. High-pressure compressor for fuel cells The storage capacity can be increased by compressing 50 Mpa or more for hydrogen storage in fuel cells.

2. Water purification device Normally, high pressure can be generated, and it is easy to send air into the deep sea. In addition, it is possible to operate with low power, and it is easy to design an automatic power supply type facility with solar power generation.

3. Power source for ships A large amount of compressed air can be supplied with low power, and it can be applied as a power source with advantages such as environmental protection and reduction of running costs by combining with solar power generation and conventional engines. .

4). Driving a car If the current drive motor is pneumatic, it can be rotated at the same power and low power. By utilizing the air compression technology of the present invention, air can be stored and manufactured easily, so there is a possibility of cost reduction and downsizing such as reduction of battery burden.

5). The air motor has a structure in which the rotor is fixed as in the prior art, and the conventional stator is a rotating body. There is no conventional difficulty such as damage to the blades even if the blades are rotated at an ultra-high speed without the conventional blades.

6). Dryers and warm air compressors generate large amounts of heat ・ Our compressors are compact, noise- and vibration-friendly, making it possible to use power-saving models that generate heat.

The piston type air compressor used in the warm dry air blowing type drying apparatus according to the present invention can also be expressed as follows. In addition, since the effect of the following invention seems to be easily conceivable from the above-mentioned content, it abbreviate | omits. In addition, it can be easily inferred that the following invention can be combined with the invention described in the claims, or the wording of the following invention can be applied.

  A cylinder member formed in the shape of a hollow column, two piston members, a first piston member and a second piston member, which are fitted in the cylinder member so as to be capable of reciprocating and sliding independently, and on the crankshaft side A first piston shaft member and a first crank arm member for connecting the piston member to the crankshaft member; a second piston shaft member and a second crank arm member for connecting the second piston member to the crankshaft member; The first piston shaft member passes through the second piston member and is connected to the second crank arm member, and the first crank arm member is more than the second crank arm member. A piston-type air compressor (A), which is arranged so that a crank radius is increased.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a detailed plan view (first embodiment) showing a piston type air compressor (air compression structure) used in a warm dry air blowing type drying apparatus according to the present invention. It is a plane detailed view (figure from an angle different from Drawing 1) showing a piston type air compressor used for a warm dry air spray type drying device concerning the present invention. It is a figure which shows operation | movement of the said air compression structure (1st step). It is a figure which shows operation | movement of the said air compression structure (2nd step). It is a figure which shows operation | movement of the said air compression structure (3rd step). It is a figure which shows operation | movement of the said air compression structure (4th step). It is a plane detailed view which shows the piston type air compressor which concerns on 2nd Example (1st step). It is a plane detailed view which shows the piston type air compressor used for the warm dry air blowing type drying apparatus which concerns on 2nd Example (2nd step). It is a plane detailed view which shows the piston type air compressor used for the warm dry air blowing type drying apparatus which concerns on 2nd Example (3rd step). It is a plane detailed drawing which shows the piston type air compressor used for the warm dry air blowing type drying apparatus which concerns on 2nd Example (4th step). It is a figure which shows the principle of the compression in the piston type air compressor used for the warm dry air blowing type drying apparatus which concerns on 2nd Example. It is a figure which shows the 1st application example of the piston type air compressor of the said (1st and 2nd) Example. In other words, it is a figure which shows a water-cooled type air compressor provided with the piston type air compressor of the said Example. In the water cooling type air compressor which is the said 1st application example, it is a figure which shows the flow of gas especially in detail. It is a figure which shows the 2nd application example of the piston type air compressor of the said Example. In other words, it is a figure which shows the hot-dry air blowing type drying apparatus which concerns on this invention provided with the piston type air compressor of the said Example. In the warm dry air blowing type drying apparatus which is the said 2nd application example, it is a figure which shows the flow of gas and a refrigerant | coolant in detail especially.

Cylinder lid 0020 Cylinder lid insertion intake valve 0030 First piston member 0040 Piston member insertion intake valve 0050 Second piston member 0060 Cylinder member with exhaust hole 0070 Cylinder lid with shaft hole and cooling hole 0080 First piston member shaft 0090 First Piston member shaft 0010 Second piston member shaft 0011 Shaft 0090 connecting rod 0012 Shaft 0080 connecting rod 0013 Shaft 0010 connecting rod 0014 Crankshaft

Claims (3)

The first piston member and the second piston member face each other in a straight line within the same cylinder member, and the piston shaft member of the first piston member penetrates the second piston member so that both piston shaft members are concentrated on one side. In a structure that can reciprocate in the same direction due to the difference in crank diameter and compress the air in two stages,
When the first piston member has an intake valve, the stationary cylinder member has an intake valve at the end, the first piston member has an intake valve, and reciprocates in cooperation with the second piston member The clearance air sandwiched between the one end of the cylinder member having the intake valve and the first piston member passes through the valve of the first piston member and reciprocates in cooperation with each other. The air compressed in one stage in the gap sandwiched between the members and compressed in one stage by continuous reciprocating motion is compressed in two stages and exhausted, and is used for the first stage compression of the cylinder member. Piston-type air compressor that can be compressed in two stages without the piping that has been used, and can be assembled with a single machine or multiple machines,
Dehumidifying means for dehumidifying the compressed air from the piston type air compressor;
An air cooling means for cooling the cylinder member constituting the piston type air compressor by the gas dehumidified by the dehumidifying means;
A warm-dry air blowing type drying apparatus comprising drying means for blowing a gas subjected to cooling by the air-cooling means by drying garbage, laundry or other moisture. The cooling means feeds the gas dried by the drying means to the outer cylinder member disposed on the coaxial outer side of the cylinder member constituting the piston-type air compressor and the gap between the outer cylinder member and the cylinder member. Information extraction pipe and the hot dry air blowing type drying apparatus according to claim 1, characterized in that it comprises. The warming and dry air blowing type drying apparatus according to claim 1 or 2 , wherein the drying means blows gas from below the moisture.

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