JP3369977B2 - Air cycle type cooling device and scroll fluid machine - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air cycle type cooling device using air as a working medium and a scroll fluid machine suitable for the cooling device.

[0002]

2. Description of the Related Art Conventionally, this kind of air cycle type cooling device is composed of a compressor, an expander, a cooler, etc., as shown as an air cycle type air conditioner in JP-A-5-223376. After the air sucked from the cooled space is compressed by the compressor, it is cooled by the cooler,
The low-temperature high-pressure air was then expanded by an expander to further lower the temperature and blown into the space to be cooled to exert the cooling effect.

[0003]

According to this structure, the problem of environmental destruction can be solved as in the conventional air conditioner using a refrigerant such as CFC, but the air compressed in the compressor expands. When expanding inside the machine, there is a volumetric efficiency of expansion in the expander, similar to the volumetric efficiency of compression in the compressor.If the compressor and expander are combined without considering it, the pre-suction pressure of the expander Since (Pes) is substantially equal to the discharge pressure (Pd) of the compressor, the discharge pressure of the compressor cannot be obtained due to the suction action from the expander side.

Focusing on the compressor alone, unless the pressure ratio between the discharge pressure and the suction pressure is properly selected, the compression work is consumed too much to increase the input, and the ratio of the output to the input COP (performance). There was also a problem that the coefficient) decreased.

The present invention has been made to solve the above-mentioned conventional technical problems, and aims to improve the cooling effect of an air cycle type cooling device and to provide a scroll fluid machine suitable for it. To aim.

[0006]

That is, an air cycle type cooling device according to the invention of claim 1 comprises air as a working medium, compression means, expansion means, and a cooler for cooling the compressed air. The ratio VC / VE of the excluded volume VC of the compression means and the excluded volume VE of the expansion means is 1.5 or more and 1.7 or less.

According to the first aspect of the invention, the excluded volume ratio VC / VE of the excluded volume VC of the compression means and the excluded volume VE of the expansion means of the air cycle cooling device is set to be 1.5 or more and 1.7 or less. Therefore, it is possible to secure the discharge pressure of the compression means, realize the efficient adiabatic expansion of air in the expansion means, and improve the cooling effect.

In the air cycle type cooling device of the invention of claim 2, in the above, the discharge pressure Pd and the suction pressure Pd of the compression means.
The pressure ratio Pd / Ps of s is 1.6 or more and 1.7 or less.

FIG. 5 shows the relationship between the pressure ratio Pd / Ps of the compression means and COP. As is clear from this figure, it can be seen that the COP decreases rapidly as the pressure ratio is increased. According to the invention of claim 2, the ratio Pd / Ps of the discharge pressure Pd of the compression means and the suction pressure Ps is set to 1.6 or more and 1.7 or less, so that the COP is not increased too much.
Can be kept high.

A scroll fluid machine according to a third aspect of the invention is
A fixed scroll having a compression element, an expansion element, and an electric element, each of which has a mirror plate and a spiral wrap standing on the mirror plate, and a fixed scroll fixed to the housing; And an oscillating scroll having a wrap of a fixed scroll and a spiral wrap that meshes with each other and a pin portion, and the electric element has a rotary shaft, and is formed at both ends of the rotary shaft. The drive parts are inserted into the pins of the orbiting scroll of the compression element and the expansion element, respectively, and the displacement volume VC of the compression element is inserted.
And the excluded volume ratio VC / VE of the excluded volume VE of the expansion element is set to be 1.5 or more and 1.7 or less.

According to a fourth aspect of the present invention, there is provided a scroll fluid machine comprising:
In the above description, the excluded volume ratio VC / VE is constituted by the height of the scroll wrap which constitutes the compression element and the expansion element.

According to a fifth aspect of the present invention, there is provided a scroll fluid machine comprising:
In Claim 3 or Claim 4, the discharge pressure Pd of the compression element
The ratio Pd / Ps between the suction pressure Ps and the suction pressure Ps is 1.6 or more and 1.7 or less.

According to the inventions of claims 3 to 5, the compression element constitutes the compression means of the air-cycle cooling device,
By configuring the expansion means of the cooling device with the expansion element, it becomes possible to enjoy the various effects described above, and a scroll fluid that is extremely suitable for the air-cycle cooling device according to claim 1 or 2. Become a machine.

Particularly, since the compression means and the expansion means can be constituted by the compression element and the expansion element included in one scroll fluid machine, it is possible to improve the productivity and reduce the cost by simplifying the number of parts and the structure. become able to. Also,
By utilizing the expansion of air, the expansion element can recover the driving force of the electric element, and it is possible to significantly improve the efficiency.

Further, according to the invention of claim 4, the excluded volume ratio VC / VE is constituted by the height of the scroll wrap constituting the compression element and the expansion element. The parameters can be made common, and the cost for designing and manufacturing can be further reduced.

[0016]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described in detail below with reference to the drawings. FIG. 1 shows a configuration diagram of an air cycle cooling device 1 to which the present invention is applied. The cooling device 1 is
For example, it cools the inside of a prefabricated freezer / refrigerator or the inside of a low-temperature tank (hereinafter referred to as a cooled space 2), and includes an oil-free scroll fluid machine 3 according to the present invention and air as a cooler. -Water heat exchanger 4 and air-air heat exchanger 6
And a dehumidifier 7 and the like.

The scroll fluid machine 3 includes a compression element (compression means) 8, an expansion element (expansion means) 9 and an electric element 1.
1 and the detailed structure thereof will be described later. An air pipe 13 is connected to the suction port 12 formed in the cooled space 2, and the air pipe 13 passes through the heat exchanger 6 and then the suction port 8S of the compression element 8.
It is connected to the.

An air pipe 14 is connected to the discharge port 8D of the compression element 8, and the air pipe 14 passes through the heat exchanger 4 and then through the heat exchanger 6 to expand the expansion element 9. It is connected to the suction port 9S. An air pipe 16 is connected to a discharge port 9D of the expansion element 9, and is connected to a blowout port 17 provided in the cooled space 2 via a dehumidifier 7.

In the cooling device 1 as described above, the electric element 11
The air in the cooled space 2 is sucked from the suction port 12 by the compression element 8 driven by, and passes through the heat exchanger 6 in the process of passing through the air pipe 13.
More inhaled and compressed. The compressed high-temperature and high-pressure air enters the air pipe 14 through the discharge port 8D, passes through the heat exchanger 4, passes through the heat exchanger 6, and is sucked into the suction port 9S of the expansion element 9.

The heat exchanger 4 is provided with a water pipe 18, and the high-temperature and high-pressure air discharged into the air pipe 14 exchanges heat with the cooling water flowing through the water pipe 18 while passing through the heat exchanger 4. And then cooled. Further, even in the process of passing through the inside of the heat exchanger 6, it is exchanged with the intake air flowing through the air pipe 13 to be further cooled.

As a result, the air exiting the heat exchanger 6 enters the expansion element 9 in a state of low temperature and high pressure. The low-temperature high-pressure air expands in the expansion element 9, and this decrease in pressure causes expansion element 9 to expand.
The air discharged from the discharge port 9D to the air pipe 16 has a lower temperature. Then, after being dehumidified through the dehumidifier 7, the air outlet 1
It is blown out into the cooled space 2 from 7. By repeating the above-described compression-cooling-expansion cycle using direct air as a medium, the inside of the cooled space 2 can be cooled to the freezing temperature.

Next, the structure of the scroll fluid machine 3 of the present invention will be described with reference to the sectional view shown in FIG. The compression element 8 of the scroll fluid machine 3 has a main housing 22 having a bearing 21 in the center, an inner housing 23 fixed to the main housing 22 with bolts, and a bolt fixed inside the inner housing 23. A first fixed scroll 24, an outer housing 26 fixed to the inner housing 23 by a bolt, and a second fixed scroll 27 fixed in the outer housing 26 by a bolt,
It is composed of an orbiting scroll 28 arranged between the fixed scrolls 24 and 27.

The main housing 22 and the inner housing 2
An O-ring 29 is interposed between the three and is sealed.
The suction port 8S is formed on the side surface of the inner housing 23, and the discharge port 8D is formed at the center of the outer housing 26.

Both fixed scrolls 24 and 27 are shown in FIG.
And the disk-shaped end plates 31, 32 as shown in FIG.
Two spiral wraps 3 provided upright on one surface 32
3, 34, and 36, 37. The fixed scrolls 24 and 27 are arranged such that the wraps 33 and 34 and the wraps 36 and 37 face each other with a predetermined gap (approximately equivalent to the thickness of the end plate 38 of the orbiting scroll 28 described later). ing. In addition, each wrap 33, 34, 3
Tip seals 48 are attached to the tips of the reference numerals 6 and 37.

On the other hand, the orbiting scroll 28 has a disk-shaped end plate 38, two spiral wraps 41, 42 and 43, 44 standing on both sides of the end plate 38, and the end plate 3.
8 is composed of a pin portion 46 projecting in the center of one surface of 8 and arm portions 47 ... A tip seal 48 is attached to the tip of each wrap 41, 42, 43, 44.

The orbiting scroll 28 includes wraps 41, 4
The protruding direction of 2 is the fixed scroll 24 direction, and the wrap 4
The fixed scroll 27 is directed in the protruding direction of 3, 44. Then, the fixed scroll 24 and the orbiting scroll 28
Means that the wraps 33 and 34 and the wraps 41 and 42 face each other and engage with each other to form a plurality of compression spaces (pressure chambers) 49 therein, and the fixed scroll 27 and the orbiting scroll 28 form the wraps 36 and 37. The wraps 43 and 44 face each other and engage with each other to form a plurality of compression spaces 49 therein.

On the surface of the main housing 22 opposite to the inner housing 23, a flange 55 at one end of the case 51 is attached with a bolt through an O-ring 50, and the electric element 11 is housed in the case 51. ing. The electric element 11 includes a stator 52 fixed in a case 51,
The rotor 53 is arranged inside the stator 52, and the rotating shaft 54 is inserted in the center of the rotor 53.

The bearing 21 has a step portion 5 on one end side of the rotary shaft 54.
Ball bearing fitted to 6 (angular ball bearing)
57 is attached. This ball bearing 57
A shaft seal 58 is attached to the orbiting scroll 28 side. The shaft seal 58 is an elastic member made of Teflon or the like, has an annular shape, and is in close contact with the peripheral surface of the rotary shaft 54. As a result, the orbiting scroll 28 side and the case 51 side are separated from each other with the shaft seal 58 as a boundary.

Reference numeral 61 denotes a drive section for transmitting the rotational force of the electric element 11 to the orbiting scroll 28, which is formed at one end of the rotary shaft 54 and is eccentric with respect to the axis thereof. This drive unit 61
Is inserted into the pin portion 46 of the orbiting scroll 28 to revolve the orbiting scroll 28.

A needle bearing 62 and a needle bearing seal 63 are attached between the drive portion 61 and the pin portion 46. Grease is enclosed in the needle bearing 62, and the needle bearing seal 63 prevents the grease from scattering. Further, 64 is a balance weight screwed to the rotary shaft 54,
65 is a terminal.

The suction port 8S formed in the inner housing 23 communicates with the compression space 49 outside the fixed scrolls 24, 27 and the orbiting scroll 28. The discharge port 8D formed in the outer housing 26 communicates with the central compression space 49. Further, 66 is an eccentric shaft that revolves the orbiting scroll 28 on a circular orbit so as not to rotate with respect to the fixed scrolls 24 and 27.

In this case, the eccentric shaft 66 is provided at four locations on the outer housing 26, one end of which is fixed to the outer housing 26 through ball bearings 67, and the other end of which is the arms 47 of the orbiting scroll 28. Are fixed via ball bearings 68. 69
Is a cover for covering the mounting portion of the eccentric shaft 66.

An oil passage 7 is provided in the main housing 22.
1 is formed, one end of this oil passage 71 communicates with the outside through a supply hole 72 on the upper surface of the main housing 22, and the other end reaches the ball bearing 57. Then, the oil supplied from the supply hole 72 is supplied to the ball bearing 57 via the oil passage 71 and lubricated, and then the case 51
Outflow hole 73 formed in the bottom surface of the main housing 22 near
Is discharged from the outside. At this time, heat generated by each device such as the electric element 11 is also taken out. This oil is blocked by the shaft seal 58 from entering the orbiting scroll 28 side.

On the other hand, the expansion element 9 of the scroll fluid machine 3 has a bearing 74 in the center, and a main housing 77 fixed to the flange 75 at the other end of the case 51 with an O-ring 76 by a bolt. An inner housing 78 bolted to the main housing 77, a first fixed scroll 79 bolted to the inner housing 78, and an outer housing 81 bolted to the inner housing 78. And a second fixed scroll 82 fixed in the outer housing 81 with bolts,
It is composed of an orbiting scroll 83 arranged between the fixed scrolls 79 and 82.

Main housing 77 and inner housing 7
An O-ring 84 is interposed between the eight and sealed.
The discharge port 9D is formed on the side surface of the inner housing 78, and the suction port 9S is formed at the center of the outer housing 81.

Although the fixed scrolls 79 and 82 and the orbiting scroll 83 have a structure in which the wrap size is reduced as described later, the fixed scroll 2 of the compression element 8 is described.
4, 27 and the orbiting scroll 28 are basically the same. That is, both the fixed scrolls 79 and 82 are also disk-shaped end plates 86 and 87, as shown in FIG.
7, two spiral wraps 88 erected on one surface of 7,
It is composed of 89, 91, and 92. And
The fixed scrolls 79 and 82 are arranged so that the wraps 88 and 89 and the wraps 91 and 92 are opposed to each other with a predetermined gap (approximately equivalent to the thickness of the end plate 93 of the orbiting scroll 83). A tip seal 48 is also attached to the tip of each wrap 88, 89, 91, 92.

On the other hand, as shown in FIG. 3, the orbiting scroll 83 also has a disk-shaped end plate 93, and two spiral wraps 94, 96, and 9 erected on both sides of the end plate 93.
7, 98, a pin portion 99 protruding in the center of one surface of the end plate 93, and an arm portion 10 formed by protruding four places outward.
It consists of 1 ... In addition, each lap 94, 9
Tip seals 48 are also attached to the tips of 6, 97 and 98.

The orbiting scroll 83 has wraps 94, 9
The protruding direction of 6 is the fixed scroll 79 direction, and the wrap 9
The protruding direction of 7, 98 is the fixed scroll 82 direction. Then, the fixed scroll 79 and the orbiting scroll 83
Means that the wraps 88 and 89 and the wraps 94 and 96 face each other and engage with each other to form a plurality of expansion spaces (pressure chambers) 102 therein, and the fixed scroll 82 and the orbiting scroll 83 form the wraps 91 and 92. The wraps 97 and 98 are intermeshing with each other to form a plurality of inflation spaces 102 therein.

A ball bearing (angular ball bearing) 104 fitted to the other end of the rotary shaft 54 is attached to the bearing 74. A shaft seal 106 is attached to the orbiting scroll 83 side of the ball bearing 104. The shaft seal 106 is an elastic member made of Teflon or the like, has an annular shape, and is in close contact with the peripheral surface of the rotating shaft 54. As a result, the orbiting scroll 83 side and the case 51 side are separated from each other with the shaft seal 106 as a boundary.

Reference numeral 107 denotes an electric element 11 and an orbiting scroll 8.
A drive unit that connects the drive shaft 3 and the drive unit 61. The drive unit 107 is inserted into the pin portion 99 of the orbiting scroll 83 to transmit the revolution force of the orbiting scroll 83 to the rotating shaft 54, or to transmit the rotation of the rotating shaft 54 to the orbiting scroll 83. Is.

A needle bearing 111 and a needle bearing seal 112 are provided between the driving portion 107 and the pin portion 99.
Is attached. This needle bearing 111
Is filled with grease, and the needle bearing seal 112 prevents the grease from scattering. Further, 113 is a balance weight screwed to the rotary shaft 54.

The discharge port 9D formed in the inner housing 78 communicates with the expansion space 102 outside the fixed scrolls 79 and 82 and the orbiting scroll 83. The suction port 9S formed in the outer housing 81 communicates with the central expansion space 102. Further, 114 is an eccentric shaft that revolves the orbiting scroll 83 on a circular orbit so as not to rotate with respect to the fixed scrolls 79 and 82.

In this case, the eccentric shaft 114 is provided at four locations on the outer housing 81, one end of which is fixed to the outer housing 81 via ball bearings 116.
The other ends are fixed to the respective arm portions 101 ... Of the orbiting scroll 83 via ball bearings 117.
Reference numeral 118 is a cover that conceals the mounting portion of the eccentric shaft 114.

The oil passage 1 is provided in the main housing 77.
19 is formed, one end of this oil passage 119 communicates with the outside through a supply hole 121 on the upper surface of the main housing 77, and the other end reaches the ball bearing 104. The oil supplied from the supply hole 121 is supplied to the oil passage 1
After being supplied to the ball bearing 104 via 19 and lubricated, the ball bearing 104 is discharged to the outside from an outflow hole 122 formed in the bottom surface of the case 51 near the main housing 77. At this time, heat generated by each device such as the electric element 11 is also taken out. The oil is prevented from entering the orbiting scroll 83 by the shaft seal 106.

A vacuum heat insulating panel 123 is embedded in the surface of the main housing 77 on the inner housing 78 side and is in surface contact with the inner housing 78. The vacuum heat insulating panel 123 is made by enclosing a heat insulating material in a predetermined container and evacuating it. However, the recess of the main housing 77 in the vacuum heat insulating valve 123 may be evacuated to form a vacuum chamber. It is a thing.

Here, the pressure ratio Pd / Ps between the discharge pressure Pd of the compression element 8 and the suction pressure Ps is set to 1.6 or more and 1.7 or less. Further, the excluded volume ratio VC of the excluded volume VC of the compression element 8 and the excluded volume VE of the expansion element 9 is VC /
VE is set to 1.5 or more and 1.7 or less.

When constructing the excluded volume ratio VC / VE, each wrap 3 of the compression element 8 is formed as shown in FIG.
When the heights of 3, 34, 36, 37, 41, 42, 43, and 44 are H, parameters such as the number of turns of the scroll and the radius of the base circle are unchanged, and the wraps 8 of the expansion element 9 are retained.
The height h of 8, 89, 91, 92, 94, 96, 97 and 98 is set to h <H.

As a result, the other parameters of the compression element 8 and the expansion element 9 can be made common, and the cost for designing and manufacturing the scroll can be reduced.

In the scroll fluid machine 3 configured as described above, when the electric element 11 is rotated, the rotational force of the electric element 11 is transmitted through the rotary shaft 54 to the orbiting scroll 28 of the compression element 8.
Be transmitted to. That is, the orbiting scroll 28 is driven by the drive portion 61 of the rotating shaft 54 inserted into the pin portion 46 of the scroll, and revolves on the circular orbit by the eccentric shaft 66 so as not to rotate with respect to the fixed scrolls 24 and 27. To be

Then, the fixed scrolls 24 and 27 and the orbiting scroll 28 gradually reduce the compression spaces 49, 49 formed on these scrolls from the outside to the inside, and flowed in from the suction port 8S. Compress the air. The compressed air is discharged from the discharge port 8D of the outer housing 26.

At this time, since the compression spaces 49, 49 are formed on both sides of the orbiting scroll 28, thrust force is applied to the orbiting scroll 28 from both sides.
As a result, the thrust force applied to the orbiting scroll 28 is almost offset as compared with the case where the wrap is formed only on one surface, and the force applied to the pin portion 46 is suppressed. Therefore, the overturning moment of the orbiting scroll 28 is reduced as much as possible, and the thrust bearing and the back pressure chamber can be eliminated.

Further, the fixed scrolls 24, 27 and the orbiting scroll 28 are provided with two wraps 33, 34, 36, 3, 3.
Since 7, 41, 42, 43, and 44 are formed, there are four air intake positions (one position in the case of one article), and one intake stroke per rotation is 90 Inspired every time. Furthermore, it becomes possible to reduce the swing radius of the swing scroll 28 as compared with the case of one line. As a result, the eccentric amount of the heavy object including the orbiting scroll 28 can be suppressed to be small, the centrifugal force can be suppressed, and the handling air flow rate can be increased, and the balance weights 64, 113 and the like can be downsized.
It becomes possible to realize smooth operation with little torque fluctuation.

Further, the compression space 49 is provided by the shaft seal 58.
By preventing the invasion of oil etc. into the fluid, the cleanliness of the pressure fluid (air) is maintained, and it is not necessary to remove foreign matter from the pressure fluid, and the fluid can be used directly. Become.

In particular, the pressure ratio Pd / Ps and the compression element 8
The COP (coefficient of performance) of FIG. 5 is as described above, but as described above, in the present invention, the pressure ratio Pd / Ps is 1.6 or more and 1.
Since it is set to 7 or less, the COP can be kept high without raising the pressure too much as is clear from this figure.

The high-temperature, high-pressure air discharged from the compression element 8 in this manner is cooled by the heat exchangers 4 and 6 as described above, and then becomes low-temperature, high-pressure air, and the suction port 9 of the expansion element 9 is cooled.
To S. At this time, the suction pressure of the expansion element 9 is Pes,
When the discharge pressure is Ped, Pes is approximately Pd. Further, the rotational force of the electric element 11 is transmitted to the oscillating scroll 83 of the expansion element 9 via the rotating shaft 54, and the oscillating scroll 83 is a drive unit of the rotating shaft 54 inserted into the pin portion 111 of this scroll. It is driven by 107 and is revolved on a circular orbit by the eccentric shaft 114 so as not to rotate with respect to the fixed scrolls 79 and 82.

The fixed scrolls 79 and 82 and the orbiting scroll 83 gradually expand the expansion spaces 102, 102 formed by these scrolls from the inside to the outside, and flowed in from the suction port 9S. Inflate the air. The expanded air having the lowered temperature is discharged from the discharge port 9D of the inner housing 78.

At this time, the orbiting scroll 83 also has the expansion spaces 102, 102 formed on both sides thereof, so that the thrust forces are canceled in the same manner as described above. In addition, the fixed scrolls 79 and 82 and the orbiting scroll 83 also have two wraps 88, 89, 91, 92, 94, 96, 97,
Since 98 is formed, the swing radius of the swing scroll 83 is reduced as described above. Further, the shaft seal 106 also prevents oil and the like from entering the expansion space 102.

The force generated by the expansion of the pressure fluid (air) in the expansion spaces 102, 102 is
4 and the rotation of the electric element 11 is compensated. That is, by utilizing the expansion of air, the expansion element 9 can recover the driving force of the electric element 11, and the efficiency is improved.

Further, since the vacuum heat insulating panel 123 is attached to the surface of the main housing 77 which is in contact with the inner housing 78, the heat transfer between the two is only from the slightly remaining surface contact portion. As a result, the heat transferred from the electric element 11 side to the expansion element 9 can be minimized, the adverse effect on the low temperature generation in the expansion element 9 can be minimized, and the low temperature generation efficiency can be further improved. .

In particular, the displacement volume V of the compression element 8 is as described above.
C and the excluded volume ratio VC / V of the excluded volume VE of the expansion element 9
Since E is set to 1.5 or more and 1.7 or less, it is possible to secure the discharge pressure Pd of the compression element 8 and realize efficient adiabatic expansion of air in the expansion element 9.

The low temperature air discharged from the expansion element 9 is supplied to the cooled space 2 as described above, and exerts a cooling effect.

[0062]

As described above in detail, according to the first aspect of the invention, the excluded volume VC of the compression means of the air cycle cooling device is set.
Since the excluded volume ratio VC / VE of the excluded volume VE of the expansion means is set to 1.5 or more and 1.7 or less, the discharge pressure of the compression means is secured, and efficient adiabatic expansion of air is realized in the expansion means. However, the cooling effect can be improved.

According to the second aspect of the invention, the ratio Pd / Ps of the discharge pressure Pd and the suction pressure Ps of the compression means is 1.6.
Since the above is 1.7 or less, C does not increase too much.
The OP can be kept high.

Further, according to the inventions of claims 3 to 5, the compression element constitutes the compression means of the air-cycle cooling device, and the expansion element constitutes the expansion means of the cooling device. It becomes possible to enjoy the various effects described above, and the scroll fluid machine is extremely suitable for the air cycle cooling device according to the first and second aspects.

In particular, since the compression means and the expansion means can be constituted by the compression element and the expansion element included in one scroll fluid machine, the productivity and the cost can be reduced by simplifying the number of parts and the configuration. become able to. Also,
By utilizing the expansion of air, the expansion element can recover the driving force of the electric element, and it is possible to significantly improve the efficiency.

Further, according to the invention of claim 4, the excluded volume ratio VC / VE is constituted by the height of the scroll wrap constituting the compression element and the expansion element. The parameters can be made common, and the cost for designing and manufacturing can be further reduced.

[Brief description of drawings]

FIG. 1 is a configuration diagram of an air cycle cooling device to which the present invention is applied.

FIG. 2 is a sectional view of a scroll fluid machine to which the present invention is applied.

FIG. 3 is an exploded perspective view of a fixed scroll and an orbiting scroll that constitute a compression element and an expansion element of the scroll fluid machine of FIG.

FIG. 4 is a diagram comparing the dimensional relationship of each scroll of the compression element and the expansion element of the scroll fluid machine of the present invention.

FIG. 5 is a diagram showing a relationship between a pressure ratio Pd / Ps of a compression element and COP (coefficient of performance).

[Explanation of symbols]

1 Air Cycle Cooling Device 2 Cooled Space 3 Scroll Fluid Machine 4 Water-Air Heat Exchanger 6 Air-Air Heat Exchanger 8 Compression Element 9 Expansion Element 11 Electric Element 24, 27, 79, 82 Fixed Scroll 28, 83 Swing Dynamic scroll 33, 34, 36, 37, 41, 42, 43, 44, 8
8, 89, 91, 92, 94, 96, 97, 98 Wrap 46, 99 Pin portion 54 Rotating shaft 61, 107 Drive portion 58, 106 Shaft seal

─────────────────────────────────────────────────── ─── Continuation of the front page (56) References JP-A-8-285399 (JP, A) JP-A-3-59355 (JP, A) JP-A-10-508937 (JP, A) (58) Field (Int.Cl. ⁷ , DB name) F25B 9/00 301 F25B 9/00 F25B 9/06

Claims (5)

(57) [Claims] 1. An air cycle cooling device comprising air as a working medium, a compression means, an expansion means, and a cooler for cooling the compressed air, wherein an exclusion volume VC of the compression means and an expansion volume of the expansion means. An air cycle cooling device, wherein an excluded volume ratio VC / VE of an excluded volume VE is set to be 1.5 or more and 1.7 or less. 2. A discharge pressure Pd and a suction pressure Ps of the compression means.
The air cycle type cooling device according to claim 1, wherein the pressure ratio Pd / Ps of 1.6 is set to 1.6 or more and 1.7 or less. 3. A compression element, an expansion element, and an electric element are provided, and each of the compression element and the expansion element has an end plate and a spiral wrap standing on the end plate, and is fixed to a housing. A fixed scroll, an end plate and an orbiting scroll having a spiral wrap standing on the end plate and meshing with the wrap of the fixed scroll, and a pin portion, and the electric element has a rotating shaft, The drive portions formed at both ends of the rotary shaft are inserted into the pin portions of the orbiting scroll of the compression element and the expansion element, respectively, and the exclusion volume VC of the compression element and the exclusion volume VE of the expansion element are removed. A scroll fluid machine having a volume ratio VC / VE of 1.5 or more and 1.7 or less. 4. The excluded volume ratio VC / V is determined by the height of the wrap of the scroll which constitutes the compression element and the expansion element.
The scroll fluid machine according to claim 3, wherein E is configured. 5. A discharge pressure Pd and a suction pressure Ps of the compression element.
5. The scroll fluid machine according to claim 3, wherein the pressure ratio Pd / Ps is 1.6 or more and 1.7 or less.