WO2011099052A1 - Refrigeration system - Google Patents

Refrigeration system Download PDF

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WO2011099052A1
WO2011099052A1 PCT/JP2010/000795 JP2010000795W WO2011099052A1 WO 2011099052 A1 WO2011099052 A1 WO 2011099052A1 JP 2010000795 W JP2010000795 W JP 2010000795W WO 2011099052 A1 WO2011099052 A1 WO 2011099052A1
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Prior art keywords
refrigerant
energy
tube
refrigeration system
means
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PCT/JP2010/000795
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French (fr)
Japanese (ja)
Inventor
鈴木隆
篠崎 隆
杉山 直樹
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株式会社E・T・L
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B41/00Fluid-circulation arrangements, e.g. for transferring liquid from evaporator to boiler
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B39/00Evaporators; Condensers
    • F25B39/04Condensers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B41/00Fluid-circulation arrangements, e.g. for transferring liquid from evaporator to boiler
    • F25B41/003Fluid-circulation arrangements, e.g. for transferring liquid from evaporator to boiler fluid line arrangements
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B41/00Fluid-circulation arrangements, e.g. for transferring liquid from evaporator to boiler
    • F25B41/06Flow restrictors, e.g. capillary tubes; Disposition thereof
    • F25B41/067Flow restrictors, e.g. capillary tubes; Disposition thereof capillary tubes
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2341/00Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001Ejectors not being used as compression device
    • F25B2341/0012Ejectors with the cooled primary flow at high pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2400/00General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/14Power generation using energy from the expansion of the refrigerant

Abstract

Provided is a highly-efficient refrigeration system. Specifically, provided is a refrigeration system equipped with the following components which are connected by means of an annular refrigerant pipe in the following order: a compressor; a radiator; a refrigerant liquefying means for liquefying a refrigerant by converting the pressure energy of the refrigerant into velocity energy; an energy conversion means for converting the velocity energy of the refrigerant from the refrigerant liquefying means into potential energy or work energy while maintaining the degree of dryness; and a heat absorber.

Description

Refrigeration system

The present invention relates to a refrigeration system including a refrigerant liquefaction unit for liquefying the refrigerant by converting pressure energy of refrigerant to speed energy.

Conventionally, a high-temperature high-pressure refrigerant gas discharged from the compressor of a refrigeration system comprising a condenser heat converter for low temperature refrigerant liquid, and isobaric cooling unit for cooling the equal pressure change a high-temperature high-pressure refrigerant gas, isobaric with reduced pressure and the remaining gas refrigerant is partially liquefied in the cooling unit by the acceleration phenomenon of the refrigerant, and a spiral tube to liquefy with a enthalpy reduction, reduced pressure by an acceleration phenomenon of the refrigerant of the refrigerant that has passed through the reduced pressure liquefied portion, and the enthalpy reducing condenser heat converter has been proposed configured to include a, a spiral tube which cools Te (Patent Document 1). Further, a compressor for inhaling refrigerant compressor, a radiator that performs heat radiation of the high-pressure refrigerant discharged from the compressor, vacuum inflate the refrigerant pressure energy of the high-pressure refrigerant in the radiator downstream converted to velocity energy together with the ejector for sucking the refrigerant, a compressor radiator and the branch flow path of the refrigerant flow is branched to suck led to ejector from between the radiator and the ejector refrigerant circulation path in which the refrigerant and a ejector circulates a throttle means is arranged in the branch flow path for decompressing the refrigerant flows, is disposed in the refrigerant flow downstream side of the unit throttle in the branch flow path, refrigeration cycle using an ejector comprising an evaporator for evaporating the refrigerant is proposed and that (Patent Document 2). These techniques each have a function to liquefy the refrigerant by converting pressure energy of refrigerant to speed energy, thus, without using a vacuum apparatus with the generation of frictional heat, it can realize high efficiency refrigeration system.

Patent No. 4,411,349 Publication JP 2008-8572 JP

However, when using a conventional spiral tube and an ejector as described above, since it has a large velocity energy refrigerant causes a frictional heat within the downstream refrigerant piping, the greater the degree of dryness of the refrigerant, the heat absorption amount of an endothermic portion but reduced, efficiency by that amount there was a problem to be lowered.
An object of the present invention is to solve the problems with the prior art described above, is to further provide a highly efficient refrigeration system.

The present invention includes a compressor, a radiator and a refrigerant liquefying means the pressure energy of refrigerant is converted to velocity energy to liquefy the refrigerant, position while maintaining the degree of dryness of the velocity energy of refrigerant from the refrigerant liquefied means and energy converting means for converting the energy or work energy, is characterized in that connected by refrigerant pipes to sequentially ring the heat sink.
In the present invention, since including a refrigerant liquefying means the pressure energy of refrigerant is converted to velocity energy to liquefy the refrigerant, without using vacuum apparatus with the generation of frictional heat, it is possible to realize a high efficiency refrigeration system, the refrigerant because with the energy conversion means for converting the potential energy or work energy while maintaining the degree of dryness of the velocity energy of refrigerant from the liquefaction unit, the speed energy of refrigerant is converted to potential energy or work energy, the flow rate decreases, the downstream in causing it decreases to frictionally heat a refrigerant pipe, the dryness of the refrigerant is maintained, increased amount of heat absorbed by the heat absorbing portion, it is possible to improve the efficiency by that amount.

In this case, the refrigerant the refrigerant liquefaction means utilizing choke phenomenon due to acceleration of the refrigerant under reduced pressure, and may be a spiral tube for liquefying with the enthalpy decrease.
Comprising a tube in which the energy conversion means containing a resistor, the velocity energy of the refrigerant coolant may be converted into work energy when exceeding resistor in the tube body.
May be spring biased resistor of the tube body is toward the inlet side of the tube body.
Comprising a tubular body the energy converting means accommodating the rotating body, the velocity energy of the refrigerant coolant may be converted into work energy for rotating the rotating body of the tube body.
The refrigerant liquefied means vertically provided so as to flow refrigerant from the bottom to the top, the energy converting means may convert the velocity energy of the refrigerant into potential energy.
In this case, the refrigerant liquefied means may be an ejector for converting pressure energy of refrigerant to speed energy.

In the present invention, since including a refrigerant liquefying means the pressure energy of refrigerant is converted to velocity energy to liquefy the refrigerant, without using vacuum apparatus with the generation of frictional heat, it is possible to realize a high efficiency refrigeration system, the refrigerant because with the energy conversion means for converting the potential energy or work energy while maintaining the degree of dryness of the velocity energy of refrigerant from the liquefaction unit, the speed energy of refrigerant is converted to potential energy or work energy, the flow rate decreases, the downstream without causing frictional heat by the refrigerant within the pipe, the dryness of the refrigerant is maintained, increased amount of heat absorbed by the heat absorbing portion, it is possible to improve the efficiency by that amount.

Is a block diagram showing an embodiment of the present invention. It is a P-h diagram of the refrigeration system according to an embodiment of the present invention. a ~ e is a plan view of the main components comprising the condensation heat converter. Is a block diagram showing the tube. It is a block diagram showing another tube. A ~ C are respectively Ph diagram. It is a block diagram showing another embodiment.

It will be described below with reference to the accompanying drawings an embodiment of the present invention.
In Figure 1, the refrigeration system comprises a compressor 1 and mini heat exchanger (isobaric cooling unit) 3 and the spiral tube (vacuum liquefaction unit) 6 and the spiral narrow tube (vacuum cooling unit) 8 and the tubular body 10 the evaporator 11 with the door as an element device, those refrigerant pipes equipment 2,4,13, suction tube 12, a large short tube (expansion unit) 5, the branch pipe (expansion unit) 7, connected by collecting pipe (expansion unit) 9 refrigeration function is realized by circulating a coolant in the direction of arrow 21. Incidentally, "mini" mini fan 3-1 mini heat exchanger 3, or later is the meaning of "small", used in order to clarify the features of the present invention that the condenser can be reduced as compared with the conventional there. Further, in this specification, hereinafter, collectively the equipment group 3,6,7,8,9,10 from the mini heat exchanger 3 up to the tubular body 10 is referred to as condensation heat converter 30.

Compressor 1, the evaporator 11, since those with structures and functions used in existing refrigeration systems are essentially unchanged, where a detailed description is omitted, the condensation heat which is a characteristic of this embodiment It will be described in detail converter 30.

Figure 2 is a P-h diagram of the refrigeration cycle of a refrigeration system using the condenser heat converter 30 according to this embodiment. Dashed lines indicate the conventional cycle, the solid line shows the cycle of this embodiment. In the conventional cycle, adiabatic compression by the compressor (point a ~ point b), condensed by the heat radiation of equal pressure change due to the condenser (point b ~ point c), an isenthalpic change due diaphragm phenomenon of the expansion valve (point c ~ point d), the cycle is complete by isobaric by evaporator, evaporation by heat absorption of the isothermal expansion (point d ~ point a).

In this embodiment, the compressor 1 high temperature (40 ° C. or higher) and high pressure (higher 0.6 MPa) gaseous refrigerant is discharged (point h ~ point i), mini heat which constitutes the condenser heat converter 30 part of the refrigerant in the changer 3 (5-50 wt%) is liquefied (point i ~ point j).
Although mini heat exchanger 3 in Figure 1 shows a conventional air-cooled type with an cooling fan to a pipe through which a refrigerant, not only the mini heat exchanger 3 in this type, it is needless to say may be a water cooling type other. In the condenser of the conventional refrigeration system substantially all liquefy high-temperature and high-pressure gas discharged from the compressor, but since the mini heat exchanger 3 may be liquefying a portion of the high-temperature and high-pressure gas than that, very small size is possible. When compared to the refrigeration system of the same cooling capacity with heat exchange device of the same type (condenser), a mini heat exchanger of this embodiment can be set to about 1/10 of the conventional condenser. Note that the mini heat exchanger 3 is provided with a mini fan 3-1, it can be as described below, and running if it becomes a predetermined operating condition, increase the heat exchange capacity.

Some liquefied refrigerant in the mini heat exchanger 3 enters the spiral tube 6 through the refrigerant pipe 4, a large short tube 5. Looking at the cross-sectional area of ​​the coolant channel, and the mini heat exchanger 3 as a reference, once increases at large short tube 5, the spiral tube 6, is smaller than the cross-sectional area of ​​the mini heat exchanger 3.

3 Daitan tube 5, the spiral tube 6, the branch pipe 7, the spiral narrow tube 8, and is a plan view showing the shape of a collecting pipe 9.
The dimensions of the large short tube 5 is the length L1 of the central thick portion as shown in FIG. 3 (a) is 10 ~ 50 mm, an inner diameter D1 of 8 ~ 20 mm cylindrical. Since both ends are connected to the refrigerant pipe 4 and the spiral tube 6, the shape respectively by inserting the refrigerant pipe 4 and the spiral tube 6, it has a cylindrical connection can dimensions. The inner diameter D1 of the thick portion of the center is preferably set larger than any of the inner diameter of the refrigerant pipe 4 and the spiral tube 6.
Helical tube 6 is in the form of wound capillary helically facedown as shown in FIG. 3 (b). Its inner diameter and number of turns, the refrigerating capacity, etc. of the refrigeration system, are determined from the various specifications, allowing up to 2 ~ 150 mm in inner diameter, preferably the inner diameter 2 ~ 50 mm, substantially most preferably an inner diameter 3 ~ 8 mm is there. For example, Agego of 2000cal / h of about refrigerator using Flon refrigerants R134a, inner diameter 5mm tubules, the number of turns is 23 winding in diameter 30mm spiral, the length of the capillary is 2.3 m. Incidentally, the inner diameter of the refrigerant pipe 2 and 4 7.7 mm, the inner diameter of the refrigerant pipe 13 and the suction pipe 12 is 10.7 mm.

If some liquefied refrigerant enters the spiral tube 6, the suction action and the like of the compressor 1, the refrigerant is accelerated (that acceleration phenomenon of the refrigerant), vacuum, and with the enthalpy decrease, increasing the liquefied amount almost liquefied, a medium pressure (0.4 ~ 0.6 MPa) liquid refrigerant at the outlet of the spiral tube 6 (j ~ point k point in FIG. 2). Conventional general Kyupi slurry tube is rather thin tube, when the contraction-vortex generated by squeezing the pressure fluid refrigerant lost kinetic energy of the refrigerant, but causes a pressure drop, compared to this , spiral tube 6 is very small aperture loss due to contracted flow-vortex, a small loss of kinetic energy of the refrigerant. Further, it is accelerated gas-liquid separation of the refrigerant by centrifugal force of the spiral tube, in particular adhered to the liquid phase portion are aggregated into the tube wall, the gas phase portion flows through the tube center portion, in the gas phase portion chalk phenomenon appears due to acceleration of the refrigerant, the refrigerant is liquefied with a reduced pressure and enthalpy decreased. Main cause of temperature reduction in the spiral tube within 6, the enthalpy of the refrigerant is heat energy in the helical tube 6 is converted to velocity energy, enthalpy of the refrigerant is reduced, leading to occurrence of the phenomenon of static temperature reduction it is determined that the objects. That spiral tube 6 constituting the energy conversion device that converts the enthalpy to velocity energy.
Flow rate of refrigerant in the spiral tube 6, in the design of the refrigeration system, more than twice the setting of the flow velocity of the mini heat exchanger 3 is desirable.

In this configuration, the vacuum liquefaction unit, but the spiral tube 6 wound spirally, as shown in FIG. 2, vacuum, and with the enthalpy reduction, if substantially liquefy can configure the gas refrigerant, not limited to a spiral tube, it may be meandering pipe and a straight pipe or the like. In this case, it is desirable to disposed a suitable throttle means inlet, or a plurality of locations such as the middle of the tube of the meandering tube or the straight pipe. In both vacuum liquefaction unit, by means other than heat radiation, that is, by conversion to the enthalpy of velocity energy, gas refrigerant is substantially liquified.

The refrigerant was the medium-pressure liquid refrigerant in helical tube 6 enters the spiral narrow tube 8 via the branch pipe 7. Spiral narrow tube 8, as shown in FIG. 3 (d), in a form wound capillary spirally Like the spiral tube 6. The inner diameter of the spiral narrow tube 8 is set smaller than the inner diameter of the helical tube 6. For example, the inner diameter of the spiral tube 6 is 3 if set to ~ 8 mm, an inner diameter of the spiral narrow tube 8 is desirably 1.2 ~ 3 mm. In the present embodiment, are connected to one spirally wound two parallel, may be connected to three or more in parallel, it is possible in one. Also, what is the direction of winding was connected to two series of different helical tubules, or may be in a form which was further connected in parallel. Sectional area of ​​the portion through which a refrigerant spiral narrow tube 8 (Agego the plurality are connected in parallel, the total cross-sectional area of ​​the plurality of) is preferably smaller than the cross-sectional area of ​​the screw 施状 tube 6. By reducing the cross-sectional area, as described below, the refrigerant is a medium spiral narrow tube 8 was spin rotational acceleration, since the pressure drop, the cooling effect is increased.
For example, if the 2000cal / h approximately the refrigerator, inner diameter 2.5mm of capillary, the number of turns is 19 winding, the diameter of the spiral is 15 mm, the length of the capillary is connected in parallel with two things 0.72m composed of Te.

As shown in FIG. 3 (c), the branch pipe 7 branches the refrigerant leaving the single spiral tube 6 to the two helical tubules 8. The length L2 is 10 ~ 50 mm of the main part of the branch pipe 7 (thick portion), the inner diameter D2 is substantially cylindrical 10 ~ 20 mm. Helical tube 6, both ends are spiral tube 6 connected to the spiral narrow tube 8, by inserting the spiral narrow tube 8, has a cylindrical connection can dimensions. In this embodiment, since the spiral narrow tube 8 is made of two tubular, although spiral narrow tube 8 connected side of the branch pipe 7 has two connection holes and the number of connection holes It matches the number of capillaries that make up the spiral narrow tube 8.
For example, the inner diameter D2 is preferably set larger than any of the inner diameter of the spiral tube 6 and the spiral narrow tube 8.

When substantially liquefied refrigerant enters the spiral narrow tube 8, the suction action and the like of the compressor 1, the refrigerant is accelerated (that acceleration phenomenon of the refrigerant), with reduced pressure, and enthalpy decreased, the liquid refrigerant is cooled . The spiral narrow tube 8 outlet, is depressurized and cooled to become a low temperature liquid, the pressure also becomes lowered low pressure (0.4 MPa or less) solution (point k ~ point l in Figure 2). Refrigerant in the spiral narrow tube 8, as shown in FIG. 2, changes in the state substantially along the saturated liquid line L. Compared to conventional Kyupi Lari tube, spiral narrow tube 8 is also very small aperture loss due to contraction flow-vortex, a small loss of kinetic energy of the refrigerant. Further, the gas-liquid separation of the refrigerant by centrifugal force in the spiral narrow tube 8 is promoted, in particular the liquid phase portion is adhered are collected into the tube wall, the gas phase portion flows through the tube center portion, the gas in phase portion Likewise choke phenomenon appears due to acceleration of the refrigerant, the refrigerant is liquefied with a reduced pressure and enthalpy decreased. Note that the configuration of each device, or the flow rate of the refrigerant, a change such as flow rate, position choke phenomenon appears is different. For example does not appear in the spiral tube within 6, it is conceivable to first appear led to the spiral narrow tube 8.
Main cause of temperature drop within the spiral narrow tube 8, similar to the temperature drop in the spiral tube within 6, the enthalpy of the refrigerant is heat energy is converted into velocity energy, enthalpy is reduced, the static temperature reduction it is determined that that led to the occurrence of the phenomenon.
That is, spiral narrow tube 8, similarly spiral tube 6, constitutes an energy conversion device that converts the enthalpy of the refrigerant to a speed energy.
Flow rate of the refrigerant in the spiral narrow tube 8, in the design of the refrigeration system, at least twice the flow rate of the mini heat exchanger 3, it is desirable that more than the flow velocity of the helical tube 6.

In this configuration, although the spiral narrow tube 8, reduced pressure, and with the enthalpy reduction, with the configuration of the liquid refrigerant can be cooled, not limited to a spiral shape, or a meandering pipe and a straight pipe or the like. In this case, the inlet of the meandering tube or the straight pipe, or it is desirable to disposed a suitable throttling means in a plurality of places such as in the middle of the tube. Both in this configuration, by means other than heat radiation, that is, by conversion to the enthalpy of velocity energy, the liquid refrigerant is cooled.

In this embodiment, as shown in FIG. 4, a spiral narrow tube 8, the collecting pipe 9 and the tube 10 are arranged up and down along the vertical line, is connected with the outlet to the tube 10 of the collector pipe 9 .
The tubular body 10 has a substantially cylindrical tube main body 10A which is enlarged, the tube body 10A, the inlet 10B and the outlet 10C each refrigerant pipe is connected is formed in the interior of the tube body 10A, resistor 10D as a resistance to the flow of the refrigerant is accommodated. The resistor 10D is supported by a spring 10E, and the resistor 10D flows through refrigerant against the spring force of the spring 10E, it is pressed against the outlet 10C side. In the tubular body 10, the resistor 10D becomes resistance to the flow of the refrigerant, as the flow rate of the refrigerant in the outlet 10C is substantially zero, such as the weight of the spring force and the resistor 10D of the spring 10E is set.
In this configuration, as described above, has a large velocity energy refrigerant at the outlet of the spiral narrow tube 8, if while maintaining this large velocity energy, the refrigerant flows into the downstream of the refrigerant pipe 13, causing frictional heat in the refrigerant pipe 13, correspondingly, and thus to increase the dryness of the refrigerant. That is, the refrigerant in the spiral narrow tube 8 is to the state of the state from point l of k points shown in FIG. 2, the resulting frictional heat in the refrigerant pipe 13, to increase the dryness of the refrigerant, the point Go to state of point m on after passing through the l, evaporator lowers the endothermic quantity Q1 at (heat absorbing portion) 11 in Q2, reducing the efficiency by the difference.

In this embodiment, the refrigerant becomes a low-temperature liquid by a spiral narrow tube 8, vertically arrayed tubular body along the vertical line to flow from below (energy conversion means) 10, in this tube 10. , against the spring force of the spring 10E, pushes away the resistor 10D flows out from above, during which converts the velocity energy of refrigerant to work energy (or potential energy).
That is, release velocity energy as work energy (or potential energy), the outlet 10C of the tube 10, the flow velocity is substantially zero.
According to this configuration, at the outlet 10C of the tubular body 10, the flow velocity of the refrigerant is substantially zero, without causing frictional heat in the refrigerant pipe 13, therefore, since the dryness fraction of the refrigerant is maintained, not moved to the state of the later point m which has passed through the points l, can be maintained endotherm in the evaporator (heat absorber) 11 to Q1, it is possible to maintain efficiency.
Further, when the liquid refrigerant present in the pipe main body 10A, the liquid refrigerant falls by its own weight inside the tube body 10A. The liquid refrigerant this fall, the refrigerant rises in the tube body 10A collides, by the collision, the speed energy of the refrigerant to rise is converted into work energy. Thus, through empirical testing, determine the energy content to be consumed by the collision, in consideration of this energy component at the outlet 10C as the flow rate of the refrigerant is substantially zero, the weight of the spring force and the resistor 10D of the spring 10E, such as it is desirable to set the.

In the evaporator 11, isobaric, by the heat absorption of the isothermal expansion, the refrigerant evaporates (point l ~ point h in FIG. 2), thereby the cycle of Figure 2 is completed.
In the above embodiment, the helical tube 6, and the spiral narrow tube 8 are connected in series, to enlarge the capacity of the mini heat exchanger 3, omitting the spiral tube 6 to the outlet of the heat exchange device 3 it is possible to connect the spiral narrow tube 8 directly by. In this case the efficiency improvement by connecting the tube 10 to the outlet of the spiral narrow tube 8 can be achieved.

Construction of the tubular body 10 is not limited to the above configuration, if the configuration capable of converting the speed energy of refrigerant to work energy (or potential energy), any configuration can be employed.
For example, the form of the resistor 10D is spherical, flat, polygon, may be in any form such as polygonal pyramid, the omission of the spring 10E are possible. Further, the tubular body 10 is arranged vertically above and below, the horizontal array may be a sequence such as the diagonal arrangement. Without converting velocity energy of the refrigerant to work energy, to convert only potential energy, by omitting the resistor 10D and the spring 10E, it is only necessary to sequence the tubular body 10 vertically up and down. In this case, the speed energy in the process of the refrigerant having the speed increases the tube body 10 is converted into potential energy.

Figure 5 shows an alternative form. The tube 10 is disposed the impeller 25, the shaft 26 of the impeller 25 is connected to the generator 27, the generator 27, for example, a power supply circuit of the drive motor of the compressor 1 shown in FIG. 1 ( is connected to the not shown). In this configuration, rotating the impeller 25 at a velocity energy of the refrigerant and converts the energy to work energy, by collecting the power of the generator 27 to the power supply circuit, the energy efficiency is further improved.

Figure 6A ~ 6C are respectively Ph diagram.
In FIG. 6A (conventional refrigeration cycle), the change of the point 3 to point 4 are isentropic change, since the pipe friction velocity is small, the energy equation is expressed as follows.
dh (enthalpy change) = dq (the amount of heat from the outside) -dwt (amount of work to the outside)
Therefore, the change of the point 3 to point 4 is as follows.
h 4 -h 3 = q 34 (frictional heat) -wt 34 (pressure loss)
Since heating and the pressure loss is equal due to friction, represented by an isenthalpic change as follows.
h 4 -h 3 = 0

In FIG 6B (using a helical tubules 6,8.), The change in the reduced kinetic energy influence of pipe friction is not negligible, the energy equation is expressed as follows.
dh (enthalpy change) + wdw (kinetic energy) = dq (the amount of heat from the outside) -dwt (amount of work to the outside)
Therefore, the change of the point 3 to point 3 'is as follows.
h 3 '-h 3 + {( w 3') 2 - (w 3) 2} / 2 = q 33 '( frictional heat) -wt 33' (pressure loss)
Here, at point 3 to point 3 'change of adiabatic change (q 33' = 0), speed when the speed of sound (w 3 '= w C) ,
h 3 '-h 3 + {( w C) 2 - (w 3) 2} / 2 = 0-wt 33'
Then, since the point 3 'speed in-point 4 is not changed, it is expressed by the following equation.
h 4 -h 3 '+ {( w C) 2 - (w C) 2} / 2 = 0-wt 3'4
Finally, the flow rate is zero by friction a change in the point 4 to point 4 ', adiabatic, since there is no pressure change is expressed by the following equation.
h 4 '-h 4 + {0- (wc) 2} / 2 = q 4'4 -wt 4'4 = 0 + v (P 4' -P 4) = 0
Also, since the kinetic energy by friction is changed into thermal energy,
qf = (wc) 2/2 ( frictional heat)
Therefore, h 4 '= h 4 + qf
Next, the refrigeration effect can be seen to decrease by the frictional heat qf.

In contrast, in FIG. 6C (a combination of spiral narrow tube 6,8 and the tube 10.), The change of the point 3 to point 3 'is represented as follows.
h 3 '-h 3 + {( w 3') 2 - (w 3) 2} / 2 = q 33 '-wt 33'
Here, at point 3 to point 3 'change of adiabatic change (q 33' = 0), speed when the speed of sound (w 3 '= w C) ,
h 3 '-h 3 + {( w C) 2 - (w 3) 2} / 2 = 0-wt 33'
Then, at the point 3 'to the point 4, performed external work in the tube 10, the speed is zero, is expressed by the following equation.
h 4 -h 3 '+ {0- (w C) 2} / 2 = 0-wt 3'4 -wt out
Here, considering that work to the outside is equivalent to the kinetic energy,
wt out = (w C) 2 /2
Therefore, the energy equation is as follows, never refrigerating capacity is lowered due to frictional heat.
h 4 = h 3 '-wt 3'4 = h 3 + v (P 4 -P 3')

Work to the outside, there is a way to convert the potential energy as follows.
wt out = (w C) 2 /2 = gz
Here, z is the height of the vertical direction.
Further, there is a method of converting the spring work as follows.
wt out = (w C) 2 /2 = k (l 2/2)
Here, l is the displacement of the spring, k is the spring constant.
Further, there is a way to convert potential energy and spring work as follows.
wt out = (w C) 2 /2 = k (l 2/2) + gz
Further, there is a method of converting the rotational work as follows.
wt out = (w C) 2 /2 = I (ω 2/2)
Here, I is the moment of inertia of the rotating body, ω is the angular velocity of the rotating body.

In condenser heat converter 30 in this cycle, isobaric cooling unit (mini heat exchanger 3), part of the refrigerant (5-50 wt%) liquefied (point i ~ point j), reduced pressure liquefied portion in (spiral tube 6), the refrigerant is accelerated, vacuum, and with the refrigerant enthalpy reduction, partially liquefied remaining gas refrigerant is substantially liquified (point j ~ point k), reduced pressure cooling unit (spiral in tubules 8), the refrigerant is accelerated, vacuum, and with the refrigerant enthalpy decreases, the refrigerant that is almost liquefied for subcooling (point k ~ point l), improves the COP of the refrigeration cycle. Further, since reducing the pressure of the refrigerant in the condensing heat converter 30, as in the prior art (generally, the capillary tube having an inner diameter of about 0.8mm) tubule and vacuum mechanism such as an expansion valve is not required, refrigeration It can be simplified cycle. Additionally, reduced pressure liquefied portions (helical tube 6), and vacuum cooling unit in (spiral narrow tube 8), to convert the refrigerant enthalpy is the heat energy to velocity energy, reduces the refrigerant enthalpy, occurrence of the phenomenon of static temperature reduction order to reach the, compared to the case of heat dissipation, downsizing of the heat exchanger is achieved.
In this embodiment, the condenser heat converter 30, isobaric cooling unit (mini heat exchanger 3), under reduced pressure liquefied portions (helical tube 6), and was constructed in vacuum cooling unit (spiral narrow tube 8) reduced pressure liquefied portions (helical tube 6) may constitute a plurality of spiral tubes connected in series, in this case, the j ~ point k point 2, and cycle lines with multiple bending points Become. Vacuum cooling unit (spiral narrow tube 8), a plurality of spiral tubes may be constructed by serially connecting, in this case, the point k ~ point l in FIG. 2, the cycle line with multiple bending points .

Figure 7 shows another embodiment. This cycle is a refrigeration cycle that utilizes a so-called ejector for converting pressure energy of refrigerant to speed energy.
61 represents a compressor, a radiator 62 is connected to a compressor 61, a receiver tank 63 is connected to the radiator 62. The receiver tank 63 ejector 64 is connected, together with the ejector 64, the refrigerant flowing out from the radiator 62 is decompressed and expanded, sucks the gas-phase refrigerant evaporated in the evaporator 65 to be described later from the suction unit 64A, the expansion energy the converted into pressure energy to increase the suction pressure of the compressor 61.
Refrigerant flowing from the ejector 64 is sucked into the compressor 61, which forms a refrigerant circulation path by. Between the later-described nozzle 64B of the receiver tank 63 and the ejector 64, provided with a branch channel 66 for guiding the refrigerant flow is branched ahead of the suction unit 64A, the evaporator 65 provided in the branch flow path 66 ing.

Further, the refrigerant flow upstream side of the evaporator 65, causes the refrigerant to be sucked into the evaporator 65 is reduced reliably pressure (evaporation pressure) in the evaporator 65 under vacuum, and flows into the evaporator 65 the refrigerant as a throttle means for regulating the flow rate (cooling capacity generated by the evaporator 65) is provided with a fixed throttle 67, such as a capillary tube.

Ejector 64 includes a nozzle 64B to the pressure energy of the high-pressure refrigerant flowing out of the radiator 62 (pressure head) is converted to velocity energy (velocity head) decompressing and expanding the refrigerant, suction gas phase refrigerant evaporated in the evaporator 65 mixing portion in which the suction unit 64A, while sucking the refrigerant from the suction portion 64A by high speed flow of refrigerant ejected from the nozzle 64B (jet), is mixed with the refrigerant sucked from the refrigerant and an evaporator 65 injected from the nozzle 64B for , and the speed energy of refrigerant flowing from the mixing portion is converted into pressure energy, and the like diffuser 64C for boosting the pressure of the refrigerant.
The outlet of the diffuser portion 64C tube 10 is connected, the tubular body 10 the compressor 61 is connected through the accumulator 68. Tube 10 is substantially similar structure as the above-described embodiment, a description thereof will be omitted. Incidentally, the diffuser portion 64C, and the tube 10 is preferably arranged vertically along the vertical line.
At the outlet of the diffuser portion 64C, the refrigerant has a large velocity energy, if while maintaining this large velocity energy and flows into the downstream of the refrigerant pipe 69, causing frictional heat in the refrigerant pipe 69, correspondingly, to increase the dryness of the refrigerant reduces the heat absorption amount of the evaporator 65, lowering the efficiency correspondingly.

In this embodiment, the outlet refrigerant of the diffuser portion 64C is vertically arrayed tubular body along the vertical line to flow from below (energy conversion means) 10, in this tube 10, the spring of the spring 10E against the force, it pushes away the resistor 10D flows out from above, during which converts the velocity energy of refrigerant to work energy (or potential energy).
That is, release velocity energy as work energy (or potential energy), the outlet 10C of the tube 10, the flow velocity is substantially zero.
According to this configuration, at the outlet 10C of the tubular body 10, the flow velocity of the refrigerant is substantially zero, without causing frictional heat in the refrigerant pipe 69, since the dryness fraction of the refrigerant is maintained, evaporators maintaining the heat absorption amount of 65, it can be maintained efficiently.
Construction of the tubular body 10 is not limited to the above configuration, it is sufficient convert velocity energy of refrigerant to work energy (or potential energy).

1, 61 compressor 2, 4, 10 refrigerant piping 3 mini heat exchanger 3-1 mini fan 6 spiral tube 8 spiral narrow tube 10 tube 11,65 evaporator 13,62 condenser 64 Ejector

Claims (7)

  1. A compressor,
    A radiator,
    A refrigerant liquefaction unit for liquefying the refrigerant by converting pressure energy of refrigerant to speed energy,
    And energy converting means for converting the potential energy or work energy while maintaining the degree of dryness of the velocity energy of refrigerant from the refrigerant liquefaction unit,
    Refrigeration system characterized in that it is connected by refrigerant pipes to sequentially ring the heat sink.
  2. The refrigerating system of claim 1,
    Refrigeration system characterized in that the refrigerant by utilizing the choke phenomenon due to acceleration of the refrigerant liquefied means refrigerant reduced pressure, and a spiral tube for liquefying with the enthalpy decrease.
  3. The refrigerating system of claim 1 or 2,
    Refrigeration system, characterized in that said energy conversion means comprising a housing with a tubular body resistor, converts the velocity energy of the refrigerant into the work energy when exceeding the resistor refrigerant in the tube body.
  4. The refrigerating system of claim 3,
    Refrigeration system characterized in that the resistor of the tube body is spring biased toward the inlet side of the tube body.
  5. The refrigerating system of claim 1 or 2,
    Refrigeration system, characterized in that said energy conversion means comprising a housing and a tube rotating body, converts the velocity energy of the refrigerant into the work energy when the refrigerant rotates the rotating body of the tube body.
  6. The refrigerating system of claim 1,
    The vertically arranged to flow the refrigerant on the refrigerant liquefaction means from below,
    Refrigeration system, characterized in that the energy converting means for converting the speed energy of refrigerant to the potential energy.
  7. The refrigerating system of claim 1,
    Refrigeration system wherein the refrigerant liquefaction means is ejector for converting pressure energy of refrigerant to speed energy.
PCT/JP2010/000795 2010-02-09 2010-02-09 Refrigeration system WO2011099052A1 (en)

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001200800A (en) * 2000-11-22 2001-07-27 Denso Corp Ejector
JP2006248338A (en) * 2005-03-09 2006-09-21 Denso Corp Cold storage heat exchanger equipped with ejector, expansion valve, and air-conditioner for vehicle
WO2007034939A1 (en) * 2005-09-26 2007-03-29 Hara Tech Corporation Thermal converter for condensation and refrigeration system using the same

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001200800A (en) * 2000-11-22 2001-07-27 Denso Corp Ejector
JP2006248338A (en) * 2005-03-09 2006-09-21 Denso Corp Cold storage heat exchanger equipped with ejector, expansion valve, and air-conditioner for vehicle
WO2007034939A1 (en) * 2005-09-26 2007-03-29 Hara Tech Corporation Thermal converter for condensation and refrigeration system using the same

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JPWO2011099052A1 (en) 2013-06-13 application

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