JPH05322338A - Complex pulse pipe type heat pump - Google Patents

Abstract

PURPOSE:To perform a cooling or heating operation, a freezing operation and a liquefying operation and the like by using an auxiliary driving system such as a heating system and a motor and the like by a method wherein a complex pulse pipe type heat pump is constituted under a combination of connecting a radiator, a cold heat accumulator, a heat accumulator, a heat absorber and a pulse pipe and the like between a compressed space and an expanded space. CONSTITUTION:A compressing piston 16 within a compression cylinder 17 is reciprocated by a crank shaft 14 through a connecting rod 15 so as to compress liquid within a compressing space 18. A power driving system is constructed by a radiator 19, a heat accumulator 20, a heat absorption part 21, a pulse pipe 22, a radiator 23, an expansion cylinder 25, an expansion piston 26 and an expansion space 24. A freezing generating system is constituted by a compressing space 29 defined by the compressing piston 28 reciprocated within the compression cylinder 27 through the connecting rod 15, a radiator 30, a cold heat accumulator 31, a low temperature heat absorbing part 32, a pulse pipe 33, a radiator 34, an expansion cylinder 35, an expansion piston 36 and an expansion space 37. Then, a power for a freezing generating system is supplied by the power generating system.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a composite type pulse tube heat pump, which is used as a multipurpose heat cycle such as a refrigerator, cooling and heating, freezing and drying of food and liquid / solid, liquefaction of gas, condensation and solidification of water. Available.

[0002]

2. Description of the Related Art A prior art relating to the present invention will be described with reference to FIG. 5, depending on the working fluid in the compression space 100 (required refrigeration / liquefaction temperature, output scale, and temperature of a high temperature heater heated by a flame or the like). Air, helium, argon,
Nitrogen, hydrogen, other gases and mixed gases, some liquids, hereinafter collectively referred to simply as fluids, sealed at several tens to 200 atmospheres) are compression cylinders 1 at almost normal temperature.
01, the compression piston 102 that reciprocates by connecting to a piston driving mechanism (not shown) (a crankshaft having a guide piston, a rocking plate, a rotary swash plate, a linear motor, etc.) and a fluid expansion space 103 are at about room temperature The expansion piston 105 connected to the piston drive mechanism in the expansion cylinder 104, the radiator 106 for releasing the compression heat of the fluid to the atmosphere and other fluids, the innumerable bronze and stainless steel metal mesh, and the small spheres of metal and rare earth. It is composed of a regenerator 107 packed as a regenerator material, a low temperature heat absorbing part 108, a pulse tube 109 serving as a gas piston, pipes 110 and 111, and a piston ring 112.

The pipe 111 is provided with an expansion piston 10
When the work of expansion of No. 5 is large or the temperature of the low temperature heat absorption unit 108 is high, a radiator similar to the pipe 110 is connected between the expansion space 103 and the pulse tube 109, although not shown. In addition, the compression piston 102 and the expansion piston 105
Is at the top dead center, the phase angle (crank angle) is zero.

Normally, the volume ratio Vc / Ve = Ω between the required temperature of the low temperature heat absorption part 108, the maximum scavenging volume Vc of the compression space 100 and the maximum scavenging volume Ve of the expansion space 103, and the pipe 1
Although it depends on the length of 10, 111 and the volume in the pipes 110, 111, the dead volume of the regenerator 107, the internal volume and the length of the low temperature heat absorption part 108, the expansion piston 105 is 0 degree (same phase) from the compression piston 102. ), The volume is changed by reciprocating with a phase angle advanced by about 60 degrees.

When used as a refrigerator for 80K, Ω =
7, phase angle = 30 degrees, Vc = 420 cc, rotation speed = 34
0 rpm, regenerator = stainless steel 150 mesh 800
Sheet + lead ball 0.03 cm Φ 200 g, dead volume 40 cc,
A pulse tube 2 cmΦ 25 cm long will be described.

The helium fluid having an average pressure of 20 atm in the compression space 100 is compressed by the piston drive mechanism into the compression piston 10.
When 2 goes to top dead center, it is compressed to about 30 atm, and pipe 1
10 enters the radiator 106 to radiate heat to the atmosphere and reach almost room temperature. Next, it is cooled by the regenerator material of the regenerator 107,
Expansion piston 1 with pulse tube 109 from low temperature heat absorption unit 108
Since 05 has advanced to the bottom dead center by 30 degrees, adiabatic expansion (actually a polytropic process) occurs and the expansion space 1 is expanded from the pipe 111.
03, work to push expansion piston 105 and do about 1
It becomes 5 atm.

In this process, the fluid in the pulse tube 109 plays the role of a gas piston having a temperature gradient from the low temperature of the expansion piston 105 at almost room temperature to room temperature.
The fluid temperature in the low-temperature heat-absorbing portion 108, which is the most advanced when viewed from the room temperature side of the gas piston, becomes the lowest and freezing occurs.

Further, the fluid in the expansion space 103 is the pipe 11
1, pulse tube 109, low temperature heat absorption section 108, regenerator 107
It is heated by the pipe 110 and returns to the compression space 100
The cycle ends. This is done continuously. At this time, the lowest temperature of the low temperature heat absorption part 108 becomes about 26K,
The refrigeration output at 0K was 60 W, and the figure of merit = consumed power / refrigeration output = 25. This value is close to the Stirling refrigerator, which has the highest efficiency in the refrigeration cycle.

Although Ω depends on conditions (rotation speed, required freezing / liquefaction temperature, dead volume, etc.), if Ω is set to 1.5 to 6, Ω will be 20.
It can be used as a highly efficient refrigerator or heat pump for freezing food in the 0K to 270K region, vacuum drying, air conditioning, and the like. Further, when the lead balls in the regenerator 107 were removed and the low temperature heat absorption part 108 was heated to 400K with electric power, the power consumption for the refrigerator decreased and almost disappeared, and the power generated increased as the temperature increased. Further, it has become clear that when the temperature is set to about 900 K, this configuration completely becomes a prime mover.

The greatest feature of the structure shown in FIG. 5 is that which differs greatly from the structure of the Stirling cycle. The displacer and the expansion piston, which have a relatively long shape such as the Stirling cycle, reciprocate, the manufacturing cost is high and the temperature is low, It does not require a drive mechanism. Of course, there is no need for a long-shaped expansion cylinder, which was made of a thin, low thermal conductivity material.

Therefore, in the structure shown in FIG. 5, the mechanical vibration in the low temperature heat absorbing portion 108 becomes extremely low. For example, if the cooled object of the low temperature heat absorbing portion 108 is an electronic sensor, it has been several tens of microns until now. The noise generated by mechanical vibration is eliminated, and it can now be applied to the measurement field. Mechanical vibration is approximately 5 microns vertically in and out of fluid.

Further, F which is usually impregnated with an epoxy resin is used.
The use of a displacer or expansion piston made of RP or Bakelite material not only causes mechanical vibration, but also generates impure gas and dust by contact with the material itself and the cylinder and frictional vibration to contaminate the working fluid and regenerator. Performance is deteriorated, and dust is stuck between the pipe and the cylinder and the piston, and further, the piston ring is clogged, which causes a low reliability such as stopping the refrigerator.

It is clear that the structure shown in FIG. 5 makes it possible to provide a highly reliable and low-priced machine without the need for the displacer and the expansion piston and the simple structure.

Although the analysis of the behavior of the fluid in the pulse tube 109 is insufficient in the process of the thermodynamic cycle, it is considered that the role of the displacer and the expansion piston in the case of the Stirling cycle is performed by the gas piston. ..

In the experiment, the compression space 100 and the expansion space 10
In the PV measurement in Example 3, the pressure waveform of the fluid was close to a sine wave, and was close to a Stirling cycle consisting of two equal volume processes and two equal temperature processes, and each of the four processes was a polytropic cycle with inefficiency.

In the TS diagram of FIG. 6, the fluid during operation of the refrigerator has an isothermal process in which A-B is compressed at an equal temperature while radiating heat, and B-C has a constant volume while being cooled by the regenerator 107. It is an isochoric process in which the temperature is low, and an isothermal process in which C-D expands while absorbing heat at a constant temperature. In this process, refrigeration is obtained, and the temperature rises at a constant volume while cooling the regenerator 107 at D-A. It is a process. This is an ideal cycle process of the Stirling cycle, but in the actual process of this basic type, there is inefficiency and there is inefficiency, and the chain line A-b-c-
It becomes a polytropic process like d-A.

When generating power, the direction of the cycle is reversed,
In the isothermal process while radiating heat in D-C, the isovolume process in which the temperature of the fluid rises in C-B and the isothermal process in B-A, expansion work is performed to generate power, and A-D is the isovolume process. Although the temperature returns to room temperature, each actually undergoes a polytropic cycle process and becomes d-c-b-a-d.

[0018]

By the way, it was not clear how to specifically operate and utilize the above-mentioned structure.

Therefore, the technical problem of the present invention is to establish the structure of the composite pulse tube heat pump.

[0020]

[Constitution of the invention]

[0021]

The technical means of the present invention taken to solve the above-mentioned technical problems of the present invention are: heating by flame, electric heat, etc., auxiliary driving of a motor, etc., a generator,
In the device configuration of the heat cycle for the purpose of cooling / heating, refrigeration, liquefaction of gas, and the like having other configurations, at least
Between one cylindrical or convex compression space and at least one cylindrical or convex expansion space, radiator, regenerator, regenerator, high temperature heat absorber, low temperature heat absorber, multiple pulse tubes, etc. Using at least one set of connecting
It is characterized by a device configuration capable of performing heating / cooling, freezing, gas liquefaction, etc. by using heating by electric heat or the like and auxiliary drive of a motor or the like.

[0022]

According to the above-mentioned technical means of the present invention, the structure of the power generation system and the structure of the refrigeration generation system are integrated.

[0023]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments embodying the technical means of the present invention will be described below with reference to the accompanying drawings.

In the first embodiment of FIG. 1, a crankshaft (other piston reciprocating mechanism may be used) 14 is provided with a motor and / or a generator (not shown) for smooth start-up and generation of electricity. The compression piston 16 in the compression cylinder 17 is reciprocated via the connecting rod 15 to compress the fluid in the compression space 18. Radiator 19, heat accumulator 20 packed with a large number of stacked meshes such as stainless steel and innumerable metal balls or ceramic balls as a heat storage material, heat absorption part 21 heated to high temperature by methane gas combustion or electric heat, made of metal or ceramics Pulse tube 22, radiator 23, expansion cylinder 25 at almost room temperature, expansion piston 2
A power generation system is formed from the expansion space 24 in which the fluid is expanded in 6.

A compression space 29 in which a fluid is compressed by a compression piston 28 that reciprocates in a compression cylinder 27 by a connecting rod 15, a radiator 30, a regenerator 31, a low temperature heat absorbing portion 32 for freezing and liquefying, a pulse tube 33, and heat radiation. A refrigeration generating system is constituted by the components of the container 34, the expansion cylinder 35 at almost room temperature, the expansion piston 36, and the expansion space 37.

In the present embodiment, the power generation system having the above-described configuration is configured to cover the power of the refrigeration generation system, and it is possible to operate not only one such configuration but also a plurality of configurations. Of course you can.

Reference numerals 58 and 59 are fluid pressure control valves connected between the compression spaces 18 and 29 and the radiators 19 and 30, respectively.
Reference numeral 60 is a filter for purifying the fluid to high purity, 61 is a fluid supply valve, and 62 is a connection end into a buffer tank or crankcase (not shown), which is also added in the configurations of FIGS.

Explaining the polytropic cycle including the inefficiency of the TS diagram of FIG. 2, the power generation system is AbEfA from the normal temperature of the fluid, and the refrigeration generation system is AbEfA. −
b-cd-A. This is the A-b-c-d-A of the refrigeration generation system and the d-c-b-A of the power generation system described in FIG.
It corresponds to two lines of -d.

Note that Te is the temperature at which the temperature is high, and Tc
Is the generated freezing temperature. In addition, the radiators 23 and 34 of FIG.
When the output is small, both or either may be excluded. 38 is a piston ring and 39 is a bearing.

Also, the respective compression pistons 16 and 2
8. A guide piston (not shown) may be attached to the expansion pistons 26 and 36, and the power generation system and the refrigeration generation system are not limited to one set each, but the power generation system may be at least one set. It is also possible to operate by connecting a plurality of sets to the same crankshaft or by operating a plurality of power generation systems and at least one refrigeration generation system connected to the same crankshaft. It is also easy to change the freezing temperature of each of the plurality of sets of freezing generation systems.

FIG. 3 shows a second embodiment, in which a convex piston 40 and a cylinder 41 form a power generation system compression space 43 and a refrigeration system compression space 42, and a convex expansion piston 44. The expansion space 47, 4 in each of the cylinders 45
6 is formed, and a radiator 48, a heat accumulator 49, a heat absorbing portion 50 that is heated to a high temperature, a pulse tube 51, and a heat radiation pipe 5 are formed therebetween.
2, a heat radiator 53 of a freezing generation system, a regenerator 54, a low temperature heat absorbing part 55, a pulse tube 57, and a heat radiation type pipe 57 are provided.

When a convex piston or cylinder is used, it is easy to change the volume ratio between the compression space and the expansion space, and the temperature of the fluid entering and exiting the compression space and the expansion space of the power generation system usually increases. If the upper part of the convex piston is used as the compression and expansion space of the power generation system, a temperature gradient can be applied to the convex piston to easily cope with it. Further, as compared with the configuration of FIG. 1, it is also easy to reduce the number of pistons by forming the compression space of the power generation system and the expansion space of the refrigeration generation system with one convex piston. Further, in the configuration of FIG. 1, it goes without saying that either the expansion space or the compression space can be a convex piston.

When this embodiment is used for cooling,
The radiators 19, 30, 23, 34, 48, 53 radiate heat to the atmosphere directly or indirectly, and the low temperature heat absorbing parts 32, 55 directly cool the indoor air, or the heat absorbing part 32 by another fluid. , 55 are collected and sent indoors to cool the indoor air with a fan. When used for heating, the heat of the outdoor atmosphere or the heat of the river or stratum is recovered by the low temperature heat absorbing parts 32, 55 or by using another fluid, and the radiators 19, 3 are used.
If the indoor air is heated at 0, 23, 34, 48, 53 directly or by using another fluid, it becomes a highly efficient heater due to the heat pump effect. In the heating using city gas, especially when the atmospheric temperature is low, it is highly efficient if the waste heat of the high temperature heat absorbing parts 21 and 50 to be raised is recovered. It should be noted that these cooling and heating flow passage systems are publicly known as they are the same as those of the chlorofluorocarbon heat pump, and therefore detailed description thereof will be omitted.

FIG. 4 shows a third embodiment in which the structure of FIG. 3 is further simplified and reduced in price, and the compression space 63 and the expansion space of the power generation system and the refrigeration generation system are respectively one. is there. The compression piston 64, the compression cylinder 65, the radiators 69, 74, 73, 78, the regenerator 70, the high temperature heat absorption part 71 and the pulse tube 72, the regenerator 75, the low temperature heat absorption part 76,
It comprises an expansion piston 67 and an expansion cylinder 68. In this embodiment, fluids having different temperatures enter and mix in the compression space 63 and the expansion space 66 from the refrigeration generation system and the power generation system rather than the configuration of FIG.

In the structure of each of the embodiments shown in FIGS. 1, 3 and 4, the compression and expansion piston drive mechanism includes any one of a crankshaft having a guide piston, an oscillating plate, a rotary swash plate and a linear motor. It is also possible to satisfy the function of the present invention.

[0036]

As described above, a radiator, a regenerator, a heat accumulator, a high temperature heat absorber, a low temperature heat absorber, a plurality of pulse tubes, etc. are provided between at least one compression space portion and at least one expansion space portion. The device configuration of the composite type pulse tube heat pump is established by using at least one combination for connecting
Air conditioning, freezing, gas liquefaction, etc. can now be performed using heating and auxiliary drive of a motor or the like.

[Brief description of drawings]

FIG. 1 shows a block diagram of a composite type pulse tube heat pump of a first embodiment of the present invention.

FIG. 2 shows a TS diagram in FIG.

FIG. 3 is a configuration diagram of a composite pulse tube heat pump according to a second embodiment of the present invention.

FIG. 4 is a configuration diagram of a composite pulse tube heat pump according to a third embodiment of the present invention.

FIG. 5 shows a block diagram of a prior art pulse tube cycle.

6 shows a TS diagram in FIG.

[Explanation of symbols]

 18, 29 compression space, 19, 23, 30, 34 radiator, 20 heat storage device, 21 high temperature heat absorber, 22, 33 pulse tube 24, 37 expansion space, 31 regenerator, 32 low temperature heat absorber,

Claims (2)

[Claims] 1. Heating / cooling, freezing, which comprises heating by flame, electric heat, etc., auxiliary drive of a motor, etc., a generator, and other components.
In a device configuration of a heat cycle for the purpose of liquefying gas, etc., a radiator or a regenerator is provided between at least one cylindrical or convex compression space part and at least one cylindrical or convex expansion space part. , Heat accumulator, high-temperature heat absorber, low-temperature heat absorber, use at least one combination that connects multiple pulse tubes, etc., heating by flames, electric heat, etc. and auxiliary drive of motors, etc., cooling / heating, freezing, liquefaction of gas, etc. A composite pulse tube heat pump characterized by a device configuration that enables 2. A heat cycle apparatus configuration for heating / cooling, freezing, gas liquefaction, etc. comprising heating by flame, electric heat, etc., auxiliary drive such as motor, generator, etc. , Between the compression space of the power generation system and the radiator, and between the compression space of the refrigeration generation system and the radiator, working fluid that conducts to the high-purity working fluid in the crankcase or from the buffer tank through the filter. The composite pulse tube heat pump is characterized by a device configuration in which each pressure control valve is installed and the output is adjusted by the pressure of the working fluid.