JPS6032098B2 - cold air device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a cooling air device, and particularly to a cooling air device suitable for directly cooling air without using a refrigerant.

In order to perform air conditioning, cold soot such as Freon gas is generally compressed and liquefied, and when it expands and vaporizes, it creates a low-temperature area through the heat absorption effect, and a blower blows air into this area to obtain cold air.

FIG. 1 shows a cold air system commonly used in the field of construction, which is composed of a compressor A, an evaporator B, a condenser C, a throttle valve ○, a blower E, etc.

Compressor A takes in low-pressure refrigerant gas that has become a gas in evaporator B, compresses it into a high-temperature, high-pressure state, and sends it to condenser C as it is. The high temperature and high pressure medium gas is cooled and liquefied in the condenser C. The liquefied refrigerant is depressurized by the throttle valve D, expanded, and evaporated in the evaporator B to become a gas again. At this time, heat is removed from the wall of the evaporator B, and the temperature of the air passing through the evaporator B is lowered by the blower E. Although vapor compression type cooling air devices using such refrigerants are the most widely used, ``several problems remain.

That is, none of the cold wires currently in use satisfies all of the requirements of refrigeration capacity, safety, and economic efficiency, and has some drawbacks. For example, cold butterflies, which have excellent freezing ability and are inexpensive, are poisonous, and comparatively safe bedding media are expensive. Therefore, complete leakage prevention is required, the structure is complicated, and the entire device is expensive. On the other hand, a method of compressing and expanding air to generate cold air has been considered as a simple-structured cooling air device that does not use refrigerant.

FIG. 2 is a pressure (P)-volume (V) diagram of an air expansion type refrigeration cycle known as a reverse Preyton cycle. Air with pressure Pa and volume Va at point a in Figure 2 is adiabatically compressed to the state at point b, and then cooled while maintaining the pressure Pb to contract the volume to Vc at point C. From this state, adiabatically The air is expanded to a pressure Pa.At this time, the temperature of the air drops significantly due to the cooling effect of the expansion.Figure 3 is a temperature (T) vs.
It is shown by the line connecting.

The work coefficient representing the cooling efficiency is expressed as the ratio of the consumed power represented by the areas a, b, c, and d to the absorbed heat amount represented by the areas d, a, a', and d'. The previously considered inverse Playton cycle air expansion cooling device is based on the above principle, but as is clear from Figure 3, if you try to increase the amount of absorbed heat, the power consumption will increase even more. However, in order to obtain the necessary cooling capacity, a large amount of air must be flowed, which is not economical. The purpose of the present invention is to solve the above-mentioned problems by using a multi-stage vane compressor, cooling air through a cooling device during compression, and compressing it in a nearly isothermal state. The object of the present invention is to provide a cooling air device that reduces the power required for compression, effectively creates low temperatures through adiabatic expansion, and is highly efficient and does not require soot.

Hereinafter, one embodiment of the present invention will be described in detail with reference to FIG. 4.

The compression device 1 is composed of a plurality of vane type compressors 4, 5, and 6 from the first stage to the final stage (third stage in FIG. 4), and the first stage compressor 4 has a suction port S. Also, the final stage compressor 6
are each equipped with one discharge port DoJ. 1st stage compressor 4
And the second stage compressor 5 has intermediate discharge ports ○, . , D skin D,
3, D, 4 and D2,, D22, D23, D Leopard, and the second stage compressor 5 and third stage compressor 6 are equipped with intermediate suction OS2,, S2, S crab, S24 and S3,, S Thin S
33 and S34. These mutually adjacent intermediate discharge ports D, . and D2. ,D,2 and ○,3,D.
3 and D. 4 and D2, and D22, D2 and D23,
One or more vanes 1 and 12 are always interposed between D23 and D24, and intermediate suction OS2, S2, S2
2 and S23, between S23 and S24, and between S3 and S32
, S32, and one or more vanes 112 and 113 are always interposed between the S spot and S34.

Also, intermediate discharge ports D, . , D, 2, D, 3, D, 4 and the corresponding intermediate suction ports S2, , S22, S23, S, and between the intermediate discharge ports D2,, D22, D23, D and the corresponding intermediate suction ports. Intermediate intake port S3,, S32, S crucian carp S3
4 are connected to pipe groups P, . ,P,2,P,3,P,4 and P illusion,
Connected by P foundation, P23, P24. The expansion device 2 includes a vane type expander 9 having one supply air □S■ and one exhaust port Doo, and the supply air □Soo and the discharge port Do of the final stage compressor 6 are connected by a pipe P3. .

The drive unit 3 connects the compression device 1 and the expansion device 2 to a drive shaft 101.
Therefore, they are configured so that they can be linked. The effects of the above configuration will now be explained.

First, when the drive device 3 rotates in the direction of the arrow, the compressors 4, 5, 6 and the expander 9 all begin to rotate in the direction of the arrow via the drive shaft 10, which will be explained sequentially starting from the first stage compressor 4.
In the first stage compressor 4, air is sucked in through the suction port So and compressed sequentially, and the air in the compression process is transferred to the intermediate discharge ports D, . , D, 2, D, 3, D, and 4 are sequentially discharged.

These discharge ports D, . , D,2, D,3, D,4 are discharged from pipes P, . , P, 2, P, PU P, 4, and is cooled by the cooling device 7 on the way, and is then cooled by the intermediate suction port S2, , S22, S24 of the second stage compressor 5.
guided by. At this time, the intermediate discharge port D of the first stage compressor 4,
．． Since the vane 111 is always interposed between D, 2, D, 2 and D, 3, D, 3 and O, 4, air having different compression ratios is discharged. This air with different compression ratios is supplied to the intermediate suction port S side S22, S of the second stage compressor 5.
23, made by S, is compressed again and discharged from intermediate discharge ports D2, , D22, D23, and D24 at each compression stage. Also in this second stage compressor 5, the intermediate suction OS
Since vanes 1 1 2 are always interposed between 2 and S22, S22 and S23, S23 and S, and between intermediate discharge port D and D22, D2 and D23, and D23 and D24, The compressed air of each compression stage does not mix. Second
Intermediate discharge port D side of stage compressor 5 D22, D23, D24
The compressed air discharged from the pipes P2, , P
22, P23, and P24, and is cooled by the cooling device 8 on the way, and is then cooled by the intermediate suction OS skin of the third stage compressor 6.
Guided to S spot, S34.

In this third stage compressor 6, that is, the final stage compressor, the compressed air is again compressed at each compression stage, and high-pressure compressed air is discharged from the discharge port Do. In this way, the first stage,
In each of the second stage and third stage compressors 4, 5, and 6, compressed air with different compression ratios is independently guided to the pipe,
Since it passes through the cooling device 7 or 8 on the way, the cooling effect of each can be improved.

In Figure 4, three compressors and two cooling devices were used, but
By further increasing the number of compressors and cooling devices, compression that closely approximates ideal isothermal compression can be achieved. Here, the discharge amount of the second stage compressor 5 and the third stage compressor 6 is determined by the target compression ratio rather than the intake amount of the first stage compressor 4 and the second stage compressor 5. The air is compressed to the desired pressure and discharged.

The situation of volume change between compressors will be explained with reference to FIG.

That is, the two vanes 1 of the first stage compressor 4 in FIG.
11, the rotor 121, and the casing 131, the rotation angle of the drive shaft 10 is 0 (reference).
It is maximum when the rotation angle increases, and as the rotation angle increases, the volume changes and becomes compressed as shown in the dotted image in FIG. Further, the spatial volume surrounded by one vane 112, rotor 122, and casing 132 of the second stage compressor 5 is minimum when the rotation angle of the drive shaft 10 is 0, and as the rotation angle increases, the space volume is The volume changes as does the enclosed area. On the other hand, the intermediate intermediate discharge ports ○, . ,D,2,D
, 3, D, 4 and the intermediate discharge port S of the second stage compressor 5, S
2, S23, and S24 are pipe plates, . ,P
Since they are connected by P,3 and P,4, their total volume changes as shown by the solid line. Therefore, the total amount of air that is compressed as a whole and taken in from the suction port So of the first stage compressor 4 is the intermediate discharge port D2, , D of the second stage compressor 5.
22, D23, and D24. 2nd stage compressor 5
The compressed air exchange relationship between the third stage compressor 6 and the third stage compressor 6 is also exactly the same as above. The overall compression is relatively gradual, so the pressure differential on either side of the vane is not large, reducing wear and friction losses. The details of the cooling devices 7 and 8 will be explained based on FIG.

Since the compressed air for each compression stage compressed by the first stage compressor 4 has a different compression ratio, it naturally has a different temperature. That is, intermediate discharge ports D, . The compressed air discharged from is close to room temperature, but the compression ratio of the compressed air discharged from D, 2, D, 3, D, and 4 gradually increases, so
Pipe P,. , P,2, P,3, P,4, the temperature of the compressed air flowing through them also increases. Therefore, the pipe P near normal temperature,
．． is installed at the bottom, and then P, 2, P, 3, then P, 4
The cooling effect can be increased by installing the cooling water at the top, supplying cold water from the lower water supply port 14, and discharging water from the upper drain port 15. The high-pressure compressed air thus obtained is discharged from the discharge port Do of the final stage compressor 6 and supplied to the air supply port Soo of the expander 9 of the expansion device 2.

Since this compressed air undergoes rapid adiabatic expansion within the expander 9, the temperature of the air drops significantly due to the cooling effect of the expansion, and is then discharged from the discharge port OO. As shown in FIG. 4, the expander 9 is composed of a vane 114, an o-tor 124, and a casing 134, so that the supply air □So
Drive shaft 101 due to the expansion action of the compressed air supplied to
This serves to provide rotational force. In other words, the idea is to significantly lower the temperature of the air through rapid adiabatic expansion, and at the same time to effectively utilize the energy of this compressed air and recover it as part of the driving force. The drive device 3 connects rotors 121, 122, 123, 124 via the drive shaft 10.
This power consumption is transmitted to the sixth
This will be explained in detail based on the figures and FIG.

Figure 6 is a P-V diagram showing the relationship between pressure (P) and volume (V). Compress it to the state at point b.

By adiabatically expanding the compressed air in this state to point c using an expander, the temperature of the air is significantly lowered before being discharged. Therefore, the power consumption required at this time is expressed by the area surrounded by a-b-c, which is significantly reduced compared to the area surrounded by the conventional power consumption a-b-c-d shown in Figure 2. I know that there is. FIG. 7 is a temperature (T)-entropy (S) diagram, and the power consumption is expressed by the area surrounded by a, b, and c, as described above.

This is also the conventional power consumption a, b, c, d shown in Figure 3 above.
It is clear that the area is significantly reduced compared to the area enclosed by . In this way, the power consumption required for isothermal compression is significantly reduced, and moreover, at the stage of adiabatic expansion of high-pressure compressed air, the energy of the compressed air is recovered into rotational force.

Therefore, the drive device 3 can achieve its purpose by transmitting a slight driving force equal to the difference between the power consumed by the compression device 1 and the amount of work done by the expansion device 2. The above explanation assumes that the drive shaft of multiple compressors connected to a cooling air device is common, that is, the rotors of multiple compressors all rotate at the same rotation speed. A cold air device in which the rotation speed of the compressor is varied will be explained.

In a compressor configured so that the rotational speed of a plurality of compressors is the same, the discharge amount of the m-th stage compressor is the (m-1)th stage compressor.
As described above, the suction amount must be set to be smaller than the suction amount of the stage compressor by an amount determined by the target compression ratio.

In other words, the objective could not be achieved unless all the compressors from the first stage to the final stage had different capacities. However, in the compression device according to the present invention in which a plurality of compressors have different rotational speeds, the first
It is not necessarily necessary to make the capacities of the compressors from the stage to the final stage different, and the purpose can be sufficiently achieved even if all compressors have the same capacity.

In other words, when compressors of the same capacity are used, the "(m-th)
1) The objective can be achieved by rotating the stage compressor at a revolution speed corresponding to the target compression ratio of the m-th stage compressor. Being able to use compressors of the same capacity in this way is extremely convenient in terms of replacement of consumable parts and preventive maintenance. Furthermore, as a method of making the rotational speeds of the plurality of compressors different, it is of course possible to use a plurality of transmission devices for one drive source, or to install a plurality of drive sources. The compressor installed in the vane type compressor described above is intended for the diametrically sliding vane type compressor shown in FIG. 4, but is not limited to this. Even better effects can be expected by using the axial sliding vane compressor shown in the figure.

Next, other embodiments of the present invention will be described in detail with reference to the drawings.

FIG. 8 shows the configuration of the vertical sliding vane type compression/expansion machine 16, and FIGS. 9 and 10 similarly show the air flow path. The multi-stage compression/expansion machine 16 is composed of a plurality of vane-type compression working chambers and expansion working chambers from the first stage to the final stage (third stage in FIGS. 8 to 10).

The first stage compression working chamber 17 is provided with a suction port So, and the final stage compression working chamber 19 is provided with one discharge port Do. The first stage compression working chamber 17 and the second stage compression working chamber 18 have intermediate discharge ports D, . , D, 2, D, 3, D, 4 and D2・
, D22, D23, and D are provided, and intermediate suction OS milk,
S22, S Gen, S24 and S3,, S Shigeru, S Han, S3
4 will be provided. These mutually adjacent intermediate discharge ports D, .
One or more vanes 11 are always interposed between D, 2, D, 2 and D, 3, D, 3 and D, 4, D2, and D22, D2 and D23, and D23 and D24. and intermediate inlet S
The same vane 11 is also interposed between 2 and S22, S22, S23 and S milk, S milk and S group, S32 and S33, and S33 and S34.

Also, intermediate discharge ports D, . , D side D. 3, D, 4 and the corresponding intermediate suction ports S2,, S2, S23, S24, and intermediate discharge ports D2,, D2, D fence D box and the corresponding intermediate suction ports S3,, S32 ,S33,S
34 are connected to pipe groups P, . , P,2, P,3, P,4 and P2
,, P22, and are connected by the P side P24. The expansion working chamber 20 is provided with one supply air □Soo and one exhaust port Doo, and the supply air □Soo and the discharge port Do of the final stage compression working chamber 19 are connected by a pipe P3.

- the drive 3 connects the rotor 12 via the drive shaft 10;
It is constructed so that it can be rotated.

Next, the effects of the above configuration will be explained.

First, when the drive device 3 rotates, the rotor 12 is rotated in the direction of the arrow in FIG. 10 via the drive shaft 10. In the first stage compression working chamber 17, air is sucked in through the suction port So and compressed sequentially, but the air in the compression process is transferred to the intermediate discharge port D.
、． , DB, D, 3, D, and 4 are sequentially discharged.

These discharge ports D, . , D, 2, D, 3, D, 4 are discharged from pipes P, . , P mountain, P, 3, P
.
Guided by 4. At this time, intermediate discharge ports D, . and D, 2, D, 2 and D, 3, ○, 3 and D, 4
Since the vane 11 is always interposed between them, air with different compression ratios is discharged. This air with different compression ratios is supplied to the intermediate suction ports S, S22, S23, and S24 of the second stage compression working chamber 18, and is compressed again to the intermediate discharge ports D2, D22, and D23 for each compression stage.
, Discharged from D. Also in this second stage compression working chamber 18, intermediate suction ports S2 and S2, S22 and S23, S
23 and S24, and intermediate discharge ports D2 and D22,
Since the vane 11 is always interposed between D22 and D23, and between D23 and D24, the compressed air of each compression stage does not mix. The compressed air discharged from the intermediate discharge ports D2, D22, D23, and D24 of the second stage compression working chamber 18 passes through pipes P2, P22, P23, and P24, respectively, and is cooled by the cooling device 8 on the way. , intermediate suction port S3 of the third stage compressed crucian carp compression chamber 19, S32, S side S3
Guided by 4.

Even in this third stage compression working chamber 19, that is, the final stage compressor,
The compressed air is compressed again after each compression stage and is then discharged from the outlet D.
. The higher pressure compressed air is discharged. In this way, each compression working chamber 17, 18, 1 of the first stage, second stage, and third stage
At 9, the compressed air having different compression ratios is independently led to the pipes and passes through a cooling device on the way, so that the cooling effect of each can be improved.

In Figures 8 to 10, three compression working chambers and two cooling devices are used, but by further increasing the number of compression working chambers and cooling devices, it is possible to perform compression that closely approximates ideal isothermal compression. It is possible. Here, the discharge amount of the second stage compression working chamber 18 and the third stage compression working chamber 19 is higher than the intake amount of the first stage compression working chamber 17 and the second stage compression working chamber 18 at the target compression ratio. Since the pressure is set to decrease by a predetermined amount, the air is compressed to the desired pressure and discharged.

The situation of the change in air volume between the compression working chambers is the same as in the explanation with reference to FIG. 5 above.

The high-pressure compressed air obtained in this way is discharged from the discharge port Do of the final stage compression working chamber 19, and undergoes rapid adiabatic expansion within the expansion working chamber 20, so the temperature of the air is significantly reduced due to the cooling effect of the expansion. It is discharged from the discharge port Doo.

Further, the expansion chamber 20 includes vanes 11, as shown in FIG.
Since it is constituted by the rotor 12 and the casing 13, it functions to give rotational force to the drive shaft 10 by the expansion action of the compressed air supplied to the supply air □Soo. In other words, the idea is to significantly lower the temperature of the air through rapid adiabatic expansion, while at the same time effectively utilizing the energy of this compressed air and recovering it as part of the driving force. The drive device 3 applies rotational force to the rotor 12 via the drive shaft 10.

The drive device 3 can achieve its purpose by transmitting a small driving force equal to the difference between the power consumed for isothermal compression and the amount of work recovered from the energy of the compressed air. For details, see the 6th section above.
This is as explained based on the figure and FIG. Above 8th
The embodiment shown in Figures 1 to 10 is constructed with three stages of compression working chambers and two cooling devices, but by further increasing the number of compression working chambers and cooling devices, ideal isothermal compression is possible. It is possible to perform compression very close to .

In addition, since Fig. 8 shows an axially sliding blade type, the cooling air device itself could be made extremely compact.
The same objective can be achieved with a parallel multi-stage device in which the vanes slide diametrically as shown in FIG. The features of the compression device 1 and the expansion device 2 constituting the cold air device according to the present invention are summarized below.

[1} In the compressor 1, compressed air with different compression ratios is repeatedly compressed in multiple stages for each stage, and is effectively cooled by a cooling device installed midway.

Therefore, it is possible to perform a gentle compression that is very close to isothermal compression, and it is possible to significantly reduce power consumption and obtain high-pressure compressed air. (2) The expansion device 2 rapidly adiabatically expands the supplied compressed air to discharge extremely low-temperature air, and can effectively utilize the energy of the compressed air.

In other words, a portion of the torque can be recovered as rotational power, contributing to a reduction in power consumption. These devices have many excellent features.

The cold air device of the present invention, which is a main component, has the following integrated effects. '1} Since no refrigerant is used, it is safe and clean throughout the period of manufacture, use, and disposal.

'21 It is economical because it does not use expensive cold soot. '3
1. Simple structure as there is no throttle valve, evaporator, blower, etc. and less chance of failure. (41 The entire device is compact,
It occupies a small area.

■ There is no negative effect of reduced efficiency due to silk fog.

{6' It can be expected to be twice as efficient as the reverse Preyton cycle.

As is clear from the above description, the cooling air device according to the present invention can provide many excellent effects.

[Brief explanation of drawings]

Fig. 1 is an explanatory diagram of the configuration of a conventional cold air device, Figs. 2 and 6 are PV diagrams, Figs. 3 and 7 are TS diagrams,
FIG. 4 is an explanatory diagram of the configuration showing an embodiment of the present invention, FIG. 5 is an explanatory diagram of volume change of compressed air, FIG. 8 is a longitudinal cross-sectional view of a component showing another embodiment of the present invention, and FIG. 9 FIG. 10 is a sectional view of the rhombus portion, and FIG. 11 is a longitudinal sectional view of the diametrically sliding blade type parallel multi-stage compression/expansion machine. 1... Compression device, 2... Expansion device, 3... Drive device, 4, 5, 6... Compressor, 7, 8... Cooling device,
9... Expansion machine, 16... Compression and expansion machine, 17, 18
, 19... Compression working chamber, 20... Expansion working chamber. 2 figures O 3 figures 4 figures O figure O 0 figure O 7 figure O a figure

Claims (1)

[Claims] 1. Consisting of a compression device, an expansion device, and a drive device, the compression device is provided with a plurality of vane type compressors constituting the first stage to the final stage, and the first stage compressor is is provided with one or more suction ports, the final stage compressor is provided with one or more discharge ports, the m-th stage compressor is provided with an intermediate discharge port, and the (m+1) stage compressor is provided with a plurality of intermediate suction ports ( m is an integer of 1, 2...
The intermediate discharge port and the corresponding intermediate suction port are connected by a group of pipes each interposed in a cooling device, and the expansion device has air supply. A vane type expander having one port and one exhaust port is installed,
A cold-air device characterized in that the discharge port of the compression device and the air supply port of the expansion device are connected by a pipe, and the drive device is configured to be able to interlock the compression device and the expansion device. 2. A cold air device according to claim 1, characterized in that the rotation speeds of the compression device and/or the expansion device are different. 3. A cold air device according to claim 1, characterized in that either the compression device or the expansion device has a common drive shaft. 4. A cold air device according to any one of claims 1 to 3, characterized in that the compression device and/or the expansion device are axially sliding blades. 5 Consisting of a compression device, an expansion device, and a drive device, the compression device is equipped with a multi-stage compressor having a plurality of vane-type working chambers constituting the first stage to the final stage, and the first stage working chamber is is provided with an inlet port, one or more discharge ports are provided in the final stage working chamber, an intermediate discharge port is provided in the mth stage working chamber, and one or more discharge ports are provided in the mth stage working chamber, and one or more discharge ports are provided in the
A plurality of intermediate suction ports are provided in each stage working chamber (m is 1, 2
,...), one or more vanes are always interposed between the intermediate discharge port and the intermediate suction port that are adjacent to each other, and cooling is performed between the intermediate discharge port and the corresponding intermediate suction port. The expansion device is connected by a group of pipes interposed in the device, and the expansion device includes a vane-type working chamber each having one air supply port and one exhaust port, and a discharge port of the compression device and the expansion device. 1. A cold-air device, characterized in that the air supply port of the device is connected to the device through a pipe, and the drive device is configured to be able to interlock the compression device and the expansion device. 6. A cold-air device according to claim 5, characterized in that the compression device and/or the expansion device are axially sliding blades.