JP2000356424A - Cooling apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an economical cooling apparatus capable of supplying cold air without pulsation by utilizing effectively expansion energy of an expansion machine. SOLUTION: There are disposed on a system base table 60 a plurality of single cooling apparatus each including a compressor 1, a heat exchanger, an expansion machine 22, and crank apparatuses 9a to 9c. The cooling apparatus exhausts cold air by collecting it produced by the plurality of the cooling apparatuses each of which operates at a predetermined phase difference, so that pulsation of the cold air is eliminated by collecting the pulsation motions of the cold airs produced from each cooling apparatus.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a cooling device using air as a refrigerant.

[0002]

2. Description of the Related Art In recent years, the deterioration of the environment surrounding the earth, such as ozone depletion and global warming, which are affected by chlorofluorocarbon gas, has become a serious problem. As one of the flows, the development of a clean and safe cooling device using air in the natural world as a refrigerant is progressing.

In general, a cooling device using air as a refrigerant draws and compresses outside air with a compressor, guides the compressed and high-temperature air to a heat exchanger and cools the air to near normal temperature.
This is a configuration in which this is guided to an expander for adiabatic expansion.The temperature of the air drops to a low temperature of minus several tens of degrees, and this cold air is led to a freezing room to absorb the heat of the target and freeze. I have.

[0004]

However, the above cooling device has the following practical problems. The compressor and the expander are driven by separate drive systems. The compressor needs energy to compress the outside air, and the expander also needs energy to expand the compressed air. Therefore, the power consumption is large, the running cost is high, and it is uneconomical. Pulsation may occur in the cool air based on the operation phase of the expander, and it is desired to suppress the pulsation of the cool air in order to achieve constant cooling of the target object. In the expander, the temperature of the air drops sharply to minus several tens of degrees Celsius, so the moisture contained in the air in the expander may condense and freeze on the exhaust valve of the expansion cylinder, etc., preventing the operation of the cooling device. There is. It is desired to further improve the cooling efficiency of the cooling device.

Accordingly, an object of the present invention is to provide a cooling device capable of supplying cool air which solves the above-mentioned problems.

[0006]

According to the cooling device of the present invention, as means for reducing the pulsation of cool air, one or a plurality of compression cylinders accommodating a reciprocating compression piston and an expansion piston reciprocatingly accommodated therein. A plurality of expansion cylinders, one or a plurality of crankshafts interlocked with each other and rotating in the same cycle, and a first crank mechanism that reciprocally connects the respective compression pistons via a crankpin from the crankshaft, A second crank mechanism that reciprocally connects the expansion pistons with a predetermined phase difference from the crankshaft via crankpins, a driving device that rotationally drives the crankshafts, and an intake port of the compression cylinder Compressed air that is communicated with an exhaust port that exhausts compressed air introduced inside the compression cylinder and compressed inside the compression cylinder, and an intake port of each of the expansion cylinders. A supply passage, a primary cooler disposed in the compressed air supply passage, and a plurality of exhaust ports for exhausting low-temperature air to the outside due to adiabatic expansion in each of the expansion cylinders. And a manifold.

In place of the driving device, a starting driving device for rotating the crankshaft at the time of starting and a compressed air supply source for supplying driving compressed air of a predetermined pressure to the compressed air supply passage are provided. May be.

Further, the cooling device of the present invention includes one or a plurality of compression cylinders in which a compression piston is reciprocally accommodated and an expansion piston in a reciprocally movable manner as means for preventing dew condensation and icing in the expansion cylinder. One or a plurality of expansion cylinders, one or a plurality of interlocked crankshafts, a first crank mechanism that reciprocally connects the compression pistons via the crankshaft from the crankshaft, and the crankshaft; A second crank mechanism that reciprocally connects the respective expansion pistons via a crank pin, a driving device that rotationally drives the crankshaft, and a driving mechanism that is introduced from an intake port of the compression cylinder and is inside the compression cylinder. An exhaust port for exhausting compressed compressed air, a compressed air supply passage communicating with an intake port of each of the expansion cylinders, A primary cooler disposed in an air supply passage, an air drying device disposed in an intake passage or the compressed air supply passage for introducing air into an intake port of the compression cylinder, and heat insulation in each of the expansion cylinders A cold air exhaust manifold that communicates with a plurality of exhaust ports that exhaust air that has been cooled to a low temperature by external expansion to the outside.

In the above, when the air drying device is disposed closer to the compression cylinder than the primary cooler of the compressed air supply passage, it is desirable to provide a secondary cooler between the air drying device and the compression cylinder. .

[0010] The introduction pipe for introducing air into the intake port of the compression cylinder may be open to the cool air exhaust space of the cool air exhaust manifold, and may communicate with the cool air exhaust manifold for cooling air exhaust. A part of the air in the manifold may be introduced into the compression cylinder.

An air pressure measuring sensor and an air pressure adjusting mechanism are provided in the compressed air supply passage, and a temperature measuring sensor is provided in the cold air exhaust manifold. The pressure of the compressed air sucked into the expansion cylinder may be adjusted based on the pressure measuring sensor.

It is desirable that one of the crankshafts is provided with a flywheel for ensuring the stable operation of the cooling device.

The heat insulating cylinder is preferably composed of a cylindrical body which is overlapped inside and outside, and the inner cylinder is preferably composed of stainless steel.

In addition, two cylinders each of which are opposed to each other along the same cylinder axis with the cylinder heads facing outwards are connected to each other, and the pistons of both cylinders are connected, and the cylinders are reciprocated linearly along the cylinder axis. The piston rod that moves, the central axis of the pitch circle is orthogonal to the cylinder axis, and the inner peripheral sun gear fixedly disposed parallel to the cylinder axis, and the pitch circle diameter of the inner peripheral sun gear A planetary gear having a half pitch circle diameter, meshed and arranged to be able to rotate and revolve, a crankshaft arranged to be rotatable around a central axis of a pitch circle of the inner peripheral sun gear, and An arm that protrudes in the radial direction of the crankshaft and rotatably supports the rotation shaft of the planetary gear, and pin-engages the intermediate portion of the piston rod on the circumference of the pitch circle of the planetary gear. It may be the one to provide the crank mechanism that.

[0015]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of a cooling device according to the present invention will be described below with reference to the drawings.

In the first embodiment, as shown in FIGS. 3 and 4, a compressor 1, a pipe (6, 21) as a compressed air supply passage, and a first heat exchanger 5 as a primary cooler are provided.
A single cooling unit having an expander 22, an exhaust pipe 26, a piston rod (8, 39), a crank device 9, and a drive motor 10 as a drive device is shown in FIG.
As shown in FIG. 2, three units are arranged in parallel on the system base 60, and the exhaust pipes 26 of the respective cooling units are connected to the cool air exhaust manifold 70 (see FIG. 3).

The system base 60 supports the cooling units at equal intervals in the vertical direction, and has a support arm 60a for supporting each cooling unit.

FIGS. 3 and 4 show the structure of a single cooling unit.

The compressor 1 houses a compression piston 3 in a reciprocating manner in a compression cylinder 2, an intake valve 4 for controlling the intake of outside air from the outside air introduction pipe 43 into the compression cylinder 2, and a pipe 6. And an exhaust valve 7 for controlling the exhaust of compressed air to the air. The intake valve 4 is an automatic valve that is pushed and opened by the outside air pressure, and the exhaust valve 7 is an automatic valve that is pushed and opened by a predetermined compressed air pressure. The compression piston 3 has a piston rod 8 protruding leftward in the figure and is connected to a drive motor 10 via a crank device 9. Thereby, the compression piston 3 reciprocates between the top dead center and the bottom dead center in accordance with the operation of the drive motor 10. The structure of the crank device 9 will be described later.

The first heat exchanger 5 circulates cooling water, for example, with a cooling tower (not shown). The first heat exchanger 5 cools the high-temperature compressed air sent from the compressor 1 through the pipe 6 to the cooling water. The primary heat is exchanged with near normal temperature by heat exchange. The compressed air primarily cooled in the first heat exchanger 5 is sent to an expander 22 through a pipe 21.

Although the first heat exchanger 5 is shown as being configured for one cooling unit,
In the present embodiment, the compressed air is once collected by communicating with the pipes 6 of the plurality of cooling units, the primary cooling is performed by a single first heat exchanger, and the compressed air after cooling is distributed to each of the expanders 2.
Sent to 2.

The expander 22 accommodates an expansion piston 24 in a reciprocating manner in an expansion cylinder 23 arranged on the same cylinder axis L as the compression cylinder 2 of the compressor 1. As shown in FIG. 5, the expansion cylinder 23 is an adiabatic cylinder that ensures the heat insulation of air during expansion.
A cylinder having a triple inner / outer structure. The inner cylinder 23a is made of stainless steel (small heat transfer coefficient), the outer cylinder 23b is made of aluminum alloy, and air is sealed between the inner cylinder 23a and the outer cylinder 23b. It has a configuration as described below. The expansion piston 24 has a piston rod 39 protruding rightward in the figure, and is pivotally connected to the piston rod 8 with a pin 40 so that the piston rod 39 reciprocates with the compression piston 3 with a phase difference of 180 °.

When the drive motor 10 is operated to reciprocate the compression piston 3 of the compressor 1 between the top dead center and the bottom dead center, the expansion piston 24 has the same cycle as the compression piston 3 and Reciprocate between top dead center and bottom dead center with a phase difference of 180 °.

A pipe 2 is provided at the head of the expansion cylinder 23.
An intake valve 25 for controlling the intake air from the exhaust pipe 1 and an exhaust valve 27 for controlling the exhaust of the adiabatic expanded low-temperature air to the exhaust pipe 26 are provided. The intake valve 25 and the exhaust valve 27
It is opened and closed at a predetermined timing by the valve operating mechanism 28.

The valve mechanism 28 is connected to one end of two rocker arms (29, 30) which are swingably provided by a timing belt 32 by a timing pulley 3 on the crankshaft 13 side.
Cams (37, 3) provided on cam shafts (35, 36) of timing pulleys (33, 34) rotating in synchronization with
8), the other end of the rocker arm 29 is pressed against the intake valve 25, and the other end of the rocker arm 30 is pressed against the tip of the tappet portion of the exhaust valve 27. As a result, the cam mechanism (35, 36) rotates with the cranking operation of the crank device 9, and the valve (28)
7, 38) swing the rocker arms (29, 30) at a predetermined timing to open and close the intake valve 25 and the outflow valve 27 at a predetermined timing.

The exhaust pipe 26 is provided with the cold air exhaust manifold 7.
In addition, it is combined with the exhaust pipes 26 of the other cooling units arranged in parallel by 0 and sent to a cooling object such as a freezing warehouse. The exhaust pipe 26 and the cool air exhaust manifold 70 are covered with a heat insulating material 26a and a heat insulating material 70a, respectively, in order to ensure heat insulation of the cool air exhausted from the expander 22.

The crank device 9 converts the rotational motion of the drive motor 10 into a linear reciprocating motion of the piston rod 8. As shown in FIG. 4, a crank device 9 includes a crankshaft 13 rotatably supported via a bearing 12 in a crankcase 11 and connected to a drive motor 10.
And a connecting pin 20 connected to the piston rod 8 and a planetary gear mechanism 15 interposed between the crankshaft 13 and the connecting pin 20.

Hereinafter, the crank device 9 will be described with reference to FIGS. 3, 4, 6 and 7.

The main components of the planetary gear mechanism 15 are an inner peripheral sun gear 16 having teeth on the inner peripheral surface and a planetary gear 17 having teeth on the outer peripheral surface.

The inner peripheral sun gear 16 has a central axis 16 a orthogonal to the cylinder axis L and parallel to the cylinder axis L, and the central axis 16 a of the inner peripheral sun gear 16 coincides with the rotation center of the crankshaft 13. Then, it is fixedly disposed on the crankcase 11.

The planetary gear 17 has a pitch circle diameter that is の of the pitch circle diameter of the inner peripheral sun gear 16, and is arranged so as to roll along the inner periphery of the inner peripheral sun gear 16.
The planetary gear 17 has a rotation shaft 14 rotatably connected to the center of the planetary gear 17 via a bearing 18, and a counter balancer 19 for applying a rotational inertia force to the shaft end of the rotation shaft 14.

The rotation shaft 14 of the planetary gear 17 serves as a crank pin, and is supported by an arm 13a projecting from the crank shaft 13 in the radial direction.

The connecting pin 20 is provided at a position corresponding to the intersection of the outer peripheral pitch circle of the planetary gear 17 and the cylinder axis L of the compression cylinder 2 on the side surface of the counter balancer 19. The connection pin 20 rotatably pivotally connects one end of the piston rod 8 of the compressor 1 via a bearing.

As shown in the schematic diagram of FIG. 7, in the crank device 9, as described above, the diameter of the pitch circle 17c of the planetary gear 17 of the planetary gear mechanism 15 is changed to the diameter of the pitch circle 16c of the inner peripheral sun gear 16. When the diameter of the pitch circle 17c of the planetary gear 17 coincides with the cylinder axis L as shown in FIG. 6, the pitch circle of the inner peripheral sun gear 16 and the pitch circle of the planetary gear 17 are set as shown in FIG. A connection pin 20 is provided at a point corresponding to the contact point with the piston rod 8 of the compressor 1. Thereby, the distance from the rotation center of the crankshaft 13 to the rotation shaft 14 of the planetary gear 17 and
Since the distance from the rotation shaft 14 of the planetary gear 17 to the connecting pin 20 for connecting the piston rod 8 is equal, and the planetary gear 17 rotates twice each time it revolves once, the connecting pin 20 is connected to the planetary gear 17. Is reciprocated linearly on the cylinder axis L each time it revolves once. Therefore, since the piston rod 8 reciprocates linearly with almost no swinging, a force in the radial direction is hardly applied to the compression piston 3 and the expansion piston 24 connected to the piston rod 39, so that so-called piston slap hardly occurs. Therefore, vibration, noise, cavitation, wear loss, etc. are greatly reduced.

The range of reciprocation of the piston rod is as follows.
Equal to the distance between the top dead center and the bottom dead center of the cylinder,
The pitch circle diameter of the inner peripheral sun gear 16 is set equal to the distance between the top dead center and the bottom dead center of the cylinder.

Further, in this case, the piston rod 8 and the piston rod 39 can be constituted by an integral continuous rod in principle. As a result, the dimensional error of each part is absorbed and the compression piston 3 and the expansion piston 24
Reciprocating movement is smooth.

In FIG. 1, the crank devices (9a, 9b, 9c) of the respective cooling units are inserted into the respective crankshafts 13 in order to operate the cooling units arranged in parallel with a predetermined phase difference. Pulley 50
Around one timing belt 52. The timing pulley 50 and the timing belt 52 are formed of a toothed pulley and a toothed belt so that the operation timings of the cooling units do not shift, and the timing pulley 50 and the timing belt 52 are meshed with each other to ensure the slippage. In the cooling device according to this embodiment, three cooling units are used, so that each cooling unit is set to operate with a phase difference of π / 3. The pulleys 54 and 56 in the drawing are idler pulleys, and secure a required tension to the timing belt 52. Also, as shown in FIGS. 1 and 2, the three crank devices (9a, 9b, 9c)
By providing a large flywheel 9b1 in the middle crank device 9b, the operation of the entire cooling device is stabilized. Thereby, the operation of the other crank devices 9a and 9c is changed to the middle crank device 9
The operation is led by the operation b, and is driven by a predetermined phase difference.

The operation of the cooling device according to the first embodiment will be described below.

As described above, in the compressor 1, the compression piston 3 reciprocates between the top dead center and the bottom dead center to suck and compress the outside air to send high-temperature compressed air to the first heat exchanger 5. That is, when the compression piston 3 passes through the top dead center and shifts to the bottom dead center, the air in the compression cylinder 2 is depressurized, and the intake valve 4 is pushed open by the external pressure to compress the external air. When the air is sucked into the cylinder 2 and the compression piston 3 passes through the bottom dead center and shifts to the top dead center, the air in the compression cylinder 2 is increased in pressure, so that the intake valve 4 is automatically closed and the compression cylinder 3 is closed. Compresses the air sucked into 2. At this time,
The air in the compression cylinder 2 becomes high-temperature compressed air. Next, when the compression piston 3 reaches the vicinity of the top dead center and the air in the compression cylinder 2 reaches a predetermined compressed air pressure, the compressor 1 pushes the exhaust valve 7 open by the pressure and the piping 6
Exhaust compressed air to

This high-temperature compressed air is sent to the first heat exchanger 5 through the pipe 6. As described above, the first heat exchanger 5 primarily cools high-temperature compressed air to near normal temperature by heat exchange with cooling water. The compressed air cooled here is sent to the expander 22 through the pipe 21.

The expander 22 adiabatically expands the compressed air introduced from the heat exchanger 5 and sends it to the exhaust port 26 as the expansion piston 24 reciprocates between the top dead center and the bottom dead center.
That is, the expander 22 uses the cam 37 to expand the expansion piston 24.
Opens the intake valve 25 only for a short time after passing through the top dead center to start shifting to the bottom dead center, inhales compressed air into the expansion cylinder 23, and in the process in which the expansion piston 24 reaches the bottom dead center, the expansion cylinder In 23, the compressed air is adiabatically expanded to near the atmospheric pressure. During the adiabatic expansion, the temperature of the air in the expansion cylinder 23 drops to minus several tens of degrees. Next, the expander 22 opens the exhaust valve 27 while the expansion piston 24 moves from the bottom dead center to the top dead center by the cam 38, and exhausts the cool air in the expansion cylinder 23 to the exhaust port 26.

Then, the cool air secondary cooled by the expander 22 of each cooling unit flows through the exhaust port 26 through the manifold 70.
After being sent to and joining, the heat of the frozen object is absorbed and frozen. At this time, since the cool air of the three cooling units having different phase differences is combined into one, the pulsation of the cool air generated by each of the cooling units is combined, and the combined cool of the exhaust cool air hardly occurs.

Note that the exhaust cool air is finally discharged into the cool air exhaust space 7.
1 and finally expands to the pressure of the cool air exhaust space 71. That is, the compressed air sucked into the expansion cylinder 23 is adiabatically expanded to the pressure of the cool air exhaust space 71, so that the temperature of the exhaust cold air is determined by the temperature and the pressure of the compressed air sucked into the expansion cylinder 23. In the above-described cooling unit, the compressed air is cooled to almost normal temperature by the first heat exchanger 5, so that if the pressure of the compressed air is increased, cooler cold air is obtained, and if the pressure of the compressed air is decreased,
The cold air temperature rises.

As shown in FIG. 3, as a structure for adjusting the temperature of the cool air, for example, a temperature sensor 94 is provided in the cool air exhaust manifold 70, a pressure measuring sensor 95 is provided in the pipe 21, and the temperature sensor 94 The pressure in the pipe 21 may be adjusted based on the pressure measuring sensor 95 so that required cold air is obtained. The pressure in the pipe 21 may be adjusted by, for example, providing a pressure reducing device 93 in the pipe 21 and supplying compressed air to the pipe 6 or 21 from a pressure increasing device (not shown) such as a compressor. . The pressure reducing device may adjust the pressure of the compressed air sent to the expansion cylinder 23 by exhausting the air to the outside when the pressure in the pipe 21 is equal to or higher than a predetermined pressure. Further, the pressure intensifier may, for example, supply compressed air generated by a pressure intensifying compressor that is driven at appropriate times into the pipe 6 from the pipe 92 to increase the pressure of the air in the pipe 6. . Further, the compressor can be configured to be driven with a clutch mechanism capable of operating the crankshaft 13 of the cooling unit 13 in a timely manner or to be driven by a separately driven motor as needed.

When the pressure-increasing compressor is connected to the crankshaft 13 via the clutch mechanism as described above, the expansion energy of the expander 22 can be used, so that a separate and independent motor is used as the drive source. And more heat energy can be taken from the compressed air in the expansion cylinder 23.
Colder air with a lower temperature can be created.

In this cooling device, when the compressed air is adiabatically expanded by the expander 22, the force received by the expansion piston 24 assists the compression step movement of the compression piston 3 of the compressor 1. That is, since each cooling unit is operated by the compression piston 3 and the expansion piston 24 on the same crankshaft 13, the expansion energy of the compressed air received by the expansion piston 24 is used as a part of the compression energy of the compression piston 3. This reduces the load on the drive motor 10 that supplies the drive energy.

In this cooling unit, the compression cylinder 2 and the expansion cylinder 23 are arranged on the same cylinder axis L, and the piston rod 8 of the compression piston 3 and the piston rod 39 of the expansion piston 24 are aligned on the cylinder axis L. When the expansion piston 24 moves from the top dead center to the bottom dead center, the expansion energy of the compressed air acting to press the expansion piston 24 is directly used when the compression piston 3 compresses the external air. , The energy efficiency is good and more economical.

In this cooling unit, the compressed air in the expansion cylinder 23 works as a part of the compression energy of the compressor 1, so that the air in the expansion cylinder 23 loses much heat energy. Therefore, it becomes possible to create cold air at a lower temperature.

Since the cool air adiabatically expanded in the expansion cylinder 23 is further adiabatically expanded to the pressure of the cool air exhaust space to be exhausted, the higher the pressure of the compressed air sucked into the expansion cylinder 23, the higher the pressure. On the other hand, the cooler air having a lower temperature can be obtained. On the other hand, the higher the pressure of the compressed air sucked into the expansion cylinder, the larger the expansion energy can be obtained from the expander 22. However, the load on the motor 10 does not increase so much.

The above-described cooling device can generate cool air of about minus 70 ° C., and is considered to be used for, for example, air conditioning in a freezer warehouse or cooling a cutting part of a machine tool. Among them, when used in machine tools, it is used for sending cooled air to a cutting blade to absorb frictional heat during cutting. As a result, the amount of cutting oil used can be reduced to the amount required for lubrication. Therefore, by making the cutting oil, for example, a vegetable oil that is easily decomposed, a machine tool that is easy on the environment can be produced.

Next, another embodiment according to the present invention will be described.

FIG. 8 shows a cooling device according to a second embodiment of the present invention. This cooling device is similar in overall configuration to the cooling device shown in FIGS. 1 and 2 described above.
The cooling unit is driven using external compressed air.

The cooling unit according to the second embodiment includes a pipe 21
Is connected to an introduction pipe 41 for introducing external compressed air from an external compressed air supply means (for example, a compressor (not shown) that is driven by another drive), and connects the crankshaft 13 of the crank device 9 to a starting drive device. The other configuration is the same as that of the embodiment shown in FIGS. 3 and 4.

The cooling unit of the second embodiment operates the starter motor 42 at the time of starting and introduces external compressed air from the introduction pipe 41 into the pipe 21, so that the compressor operates via the crank device 9 with the operation of the starter motor 42. The compression piston 3 of the compressor 1 is reciprocated between top dead center and bottom dead center.
The expansion piston 24 is reciprocated between a top dead center and a bottom dead center using external compressed air introduced into the expansion cylinder 23 of the expander 22 through the pipe 21 and the pipe 21. Thereby, similarly to the first embodiment, the cool air in which the outside air is cooled to minus several tens degrees is sent to the freezing room. In such an operation, once the system starts operating, even if the starter 42 is stopped, the expansion piston 24 of the expander 22 is already reciprocated at high speed by the external compressed air to adiabatically expand the compressed air. Therefore, the compression piston 3 of the compressor 1 reciprocates continuously by utilizing the energy of the adiabatic expansion of the expander 22, so that it can be driven only by the external compressed air.

In the above embodiment, the external compressed air is supplied to the pipe 21 through the introduction pipe 41, but the external compressed air may be supplied to the pipe 6 that sends the compressed air to the first heat exchanger 5.

According to this embodiment, for example, the compressor 1 and the expander 22 can be driven in conjunction with one power source of external compressed air by an external compressor (not shown), and the heat insulation of the expander 22 can be achieved. The expansion energy is effectively used as the compression energy of the compressor 1 and can be operated economically.

Although the introduction pipe 41 is connected to the pipe 21 on the downstream side of the first heat exchanger 5 in FIG. 8, the introduction pipe 41 is connected to the pipe 6 on the upstream side of the first heat exchanger 5. Even if
The same operation and effect as in FIG. 3 can be obtained.

Next, a cooling device according to a third embodiment of the present invention shown in FIG. 9 will be described.

This cooling device is different from the cooling device of the first embodiment described above in that the first cooling device 5 of the piping 21 of the cooling unit is provided.
An air dryer 61 as an air drying device and a second heat exchanger 62 are provided between the heat exchanger and the expander 22.

The air dryer 61 is provided with a filter using, for example, silica gel, activated alumina, or the like as an adsorbent, and the air in the filter is chemically reacted in the filter to be adsorbed and removed, thereby drying the air.

In the air dryer 61, heat of adsorption is generated during the adsorption reaction. The second heat exchanger 62 includes an air dryer 61 and an expander 22 to radiate the heat of adsorption.
Is provided in the pipe 21 between them. This second heat exchanger 62
It has the same configuration as the first heat exchanger 5, performs heat exchange between the cooling water and the air pipe, radiates the heat of adsorption of the air dryer 61, and lowers the temperature of the compressed air taken into the expansion cylinder 23. Things.

In this case, before the air is sent to the expansion cylinder 23, the moisture contained in the air can be removed, so that the inside of the expansion cylinder 23 or the cold air exhaust manifold 70 that hinders the operation of the cooling device is provided. The dew condensation and icing in such as can be eliminated.

The air dryer 61 may be provided in the inlet pipe 43 for introducing air into the compressor 1 or in the pipe 6 between the compressor 1 and the first heat exchanger 5. The second heat exchanger 62 is unnecessary because the air can be cooled by the heat exchanger.

Next, a cooling device according to a fourth embodiment of the present invention shown in FIG. 10 will be described.

This cooling device communicates with the introduction pipe 43 from the cool air exhaust space 71 in which the cool air exhaust manifold 70 of the cooling device of the third embodiment described above opens, and introduces air into the compression cylinder 2. An inlet pipe 72 and a second inlet pipe 73 for partially extracting cool air from the cooling exhaust manifold 70 and introducing the cool air to the compression cylinder 2 are provided.

The first inlet pipe 72 is provided with an inlet 72a in a closed space such as a freezing warehouse where a cooling device is mounted as the cool air exhaust space 71, or in the vicinity of a cool air exhaust hole opened toward a tool cutting portion. It is provided. The air introduced through the inlet is air that is dryer than the outside air due to the action of the air dryer 61. Therefore, by introducing the air into the cooling device again, the moisture in the air removed by the air dryer 61 can be reduced. Is reduced, and the heat of adsorption generated in the air dryer 61 is also reduced, so that the load on the second heat exchanger 62 or the first heat exchanger 5 can be reduced.

The second introduction pipe 73 is a pipe connecting the cooling exhaust manifold 70 and the introduction pipe 43 of the compression cylinder 2. For example, a three-way valve 74 is attached to the connection portion with the cooling / exhausting manifold 70. For example, when the pressure in the cooling / exhausting manifold 70 is higher than a predetermined pressure, or in a cold air exhaust space such as a cooling warehouse. When the temperature of the cooling air becomes lower than a predetermined temperature, for example, when the cooling air is generated more than necessary in the cooling device, the excessive cold air is introduced into the compression cylinder 2 again. Since the air introduced from the introduction port is dry and cool, the temperature of the air introduced into the compression cylinder 2 can be low and the air can be dried. Thereby, the burden on the first heat exchanger 5, the air dryer 61, and the like can be reduced. Also,
As shown by the broken line 74a in FIG. And a part of the created cold air may be used for cooling the cooling water and then introduced into the compression cylinder.

The above-described embodiments merely show preferred specific examples of the present invention, and the present invention is not limited to these embodiments, and various design changes may be made within the scope of the technical idea. Is possible.

In each of the above-described embodiments, a crank device provided with a planetary gear mechanism is used. However, the present invention is not limited to such a crank device.
Even when the crankshaft of the crank device provided in the compression cylinder and the crankshaft of the crank device provided in the expansion cylinder are configured separately, for example, each crankshaft is interlocked by power transmission means such as a belt or a coupling. With this configuration, the expansion energy in the expander can be effectively used as the compression energy in the compressor.

[0070]

The cooling device according to the present invention collectively exhausts the cool air generated by a plurality of cooling units operating with a predetermined phase difference, so that the pulsation generated in the cool air generated by each cooling unit is synthesized. Thus, pulsation can be eliminated in the exhaust cool air.

Further, the driving of the cooling device is such that the starting driving device provided on the crankshaft of the cooling unit and the driving compressed air are supplied to the compressed air supply passage.
It can be driven only by the driving compressed air. The driving of the cooling unit can be made efficient.

Further, since the air drying device is provided in the introduction passage for introducing air into the compression cylinder and the compressed air supply passage communicating the exhaust hole of the compression cylinder with the intake hole of the expansion cylinder, the air drying device is provided before the expansion stroke of the compressed air. By removing moisture in the air, dew condensation and icing in the expansion cylinder and the like can be prevented.

Further, by providing a cool air exhaust manifold and an inlet pipe for introducing air from the cool air exhaust space to the compression cylinder, and obtaining a part of the air to be introduced into the compression cylinder from these places, an air drying device or a heat The load on the exchanger can be reduced.

By providing a pressure measurement sensor and a pressure adjustment mechanism in the compressed air supply passage and a temperature measurement sensor in the cold air exhaust manifold, the expansion cylinder is provided based on the temperature measurement sensor and the pressure measurement sensor. By adjusting the pressure of the compressed air to be taken into the air, it is possible to obtain cold air at a required temperature.

Each cooling unit is linked by linking means for linking the crank units of each cooling unit, and one of the cooling units is provided with a large flywheel, so that the operation of the other crank units is large. Since the operation is led by the operation of the crank device provided with the flywheel and driven synchronously with a predetermined phase difference, the cost can be reduced as compared with the case where the flywheel is provided in each crank device.

Further, since the expansion cylinder of the expander in the cooling unit is constituted by an adiabatic cylinder having good heat insulation, the adiabatic expansion in the expander is efficiently performed, which is economically advantageous.

Further, when the crank device is provided with a planetary gear mechanism and the piston rods of the two cylinders are connected linearly, piston slap hardly occurs and vibration, noise, cavitation, wear loss and the like are greatly reduced. You. Further, the adiabatic expansion energy of the expander can be more effectively used as the compression energy of the compressor.

[Brief description of the drawings]

FIG. 1 is a drawing showing an overall structure of a cooling device according to a first embodiment of the present invention.

FIG. 2 is a drawing showing the overall structure of the cooling device according to the first embodiment of the present invention.

FIG. 3 is an essential part longitudinal cross sectional view showing the structure of a single cooling unit according to the first embodiment of the present invention.

FIG. 4 is a cross-sectional view of a main part of FIG.

FIG. 5 is a longitudinal sectional view of the expansion cylinder according to the first embodiment of the present invention.

FIG. 6 is a schematic diagram of a crank device according to the first embodiment of the present invention.

FIG. 7 is a schematic diagram of a crank device according to the first embodiment of the present invention.

FIG. 8 is a longitudinal sectional view of a main part of a single cooling unit according to a second embodiment of the present invention.

FIG. 9 is a longitudinal sectional view of a main part of a single cooling unit according to a third embodiment of the present invention.

FIG. 10 is a longitudinal sectional view of a main part of a single cooling unit according to a third embodiment of the present invention.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Compressor 2 Compression cylinder 3 Compression piston 4 Intake valve 5 First heat exchanger 6 Piping 7 Exhaust valve 8 Piston rod 9 Crank device 10 Drive motor 13 Crankshaft 13a Arm part 14 Rotation axis 15 Planetary gear mechanism 16 Inner peripheral sun gear 17 Planetary gear 20 Connecting pin 22 Expander 23 Expansion cylinder 24 Expansion piston 25 Intake valve 26 Exhaust pipe 27 Exhaust valve 28 Valve mechanism 31, 33, 34 Timing pulley 32 Timing belt 37, 38 Cam 39 Piston rod 42 Cell motor 43 Introducing pipe 50 Timing pulley 52 Timing belt 54, 56 Idler pulley 60 System base 61 Air dryer 62 Second heat exchanger 70 Cold air exhaust manifold 71 Cold air exhaust space 72 First introduction pipe 73 Second introduction pipe

Claims (10)

[Claims] A plurality of compression cylinders accommodating a compression piston reciprocally; a plurality of expansion cylinders accommodating an expansion piston reciprocally; A first crank mechanism that reciprocally connects the compression pistons via a crankpin from the crankshaft via a crankpin; and a predetermined phase difference between the respective expansion pistons via the crankpin from the crankshaft. A second crank mechanism connected so as to be able to reciprocate; a drive device for rotating each of the crankshafts; and an exhaust for exhausting compressed air introduced from an intake port of the compression cylinder and compressed inside each of the compression cylinders. A primary air cooler disposed in the compressed air supply passage; Cooling device, characterized in that it comprises a cold air exhaust manifold that communicates a plurality of exhaust ports for exhausting air that has become a low temperature to the outside by adiabatic expansion within the respective expansion cylinders. 2. A driving device for starting which rotates the crankshaft at the time of starting and a compressed air supply source which supplies driving compressed air of a predetermined pressure to the compressed air supply passage, instead of the driving device. The cooling device according to claim 1, further comprising: 3. One or a plurality of compression cylinders accommodating a compression piston reciprocally, one or a plurality of expansion cylinders accommodating an expansion piston reciprocally, and one or a plurality of interlocking crankshafts. A first crank mechanism that reciprocates the compression pistons from the crankshaft via a crankpin; and a second crank that reciprocates the expansion pistons from the crankshaft via a crankpin. A mechanism for driving the crankshaft to rotate; an exhaust port for exhausting compressed air introduced from the intake port of the compression cylinder and compressed inside each of the compression cylinders; and an intake port for each of the expansion cylinders. And a primary cooler disposed in the compressed air supply passage, and air is supplied to an intake port of the compression cylinder. An air drying device disposed in the intake passage or the compressed air supply passage to be introduced; and a cool air exhaust communicating with a plurality of exhaust ports for exhausting air cooled to low temperature by adiabatic expansion in each of the expansion cylinders. A cooling device, comprising: a cooling manifold. 4. The air cooler according to claim 3, wherein the air cooler is disposed closer to the compression cylinder than the primary cooler of the compressed air supply passage. A cooling device, comprising: 5. An intake pipe for introducing air into an intake port of the compression cylinder opens into a cool air exhaust space of the cool air exhaust manifold, and introduces air exhausted from the cool air exhaust manifold into the compression cylinder. The cooling device according to claim 3 or 4, wherein: 6. An introduction pipe for introducing air into an intake port of the compression cylinder communicates with the cool air exhaust manifold,
6. The cooling device according to claim 1, wherein a part of the air in the cold air exhaust manifold is introduced into the compression cylinder. 7. A pressure measurement sensor and a pressure adjustment mechanism are provided in the compressed air supply passage, and a temperature measurement sensor is provided in the cold air exhaust manifold, and the temperature sensor and the pressure sensor are provided so as to obtain cold air at a required temperature. 7. The cooling device according to claim 1, wherein the pressure of compressed air taken into the expansion cylinder is adjusted based on a sensor for measuring pressure. 8. The cooling device according to claim 1, wherein a flywheel for securing a stable operation of the cooling device is provided on one of the crankshafts. 9. The cooling device according to claim 1, wherein said heat insulating cylinder is constituted by a cylindrical body which is overlapped inside and outside, and said inner cylinder is constituted by stainless steel. 10. The two cylinders each having two cylinder heads facing each other facing the outside along the same cylinder axis, connecting the pistons of both cylinders, and linearly reciprocating along the cylinder axis. A piston rod that moves, an inner sun gear fixedly disposed parallel to the cylinder axis and a center axis of the pitch circle orthogonal to the cylinder axis between the two cylinders; A planetary gear having a half pitch circle diameter with respect to the pitch circle diameter, meshing and being arranged to be able to rotate and revolve, and is arranged rotatably around the central axis of the pitch circle of the inner peripheral sun gear. A crankshaft; and an arm protruding in a radial direction of the crankshaft to rotatably support a rotation shaft of the planetary gear, wherein the piston rod is provided on a circumference of a pitch circle of the planetary gear. The cooling device according to any one of claims 1 to 9, further comprising a crank mechanism for pin-engaging the intermediate portion.