KR100520100B1 - refrigeration system - Google Patents

Abstract

The present invention relates to a refrigeration system, and in particular, since the mutual energy is the same from high pressure to low pressure to low pressure to high pressure, using this to improve the performance and energy saving of the refrigerator using a refrigerant circulation device pressure loss from high pressure to low pressure By using the refrigerant circulation system that exchanges the mutual energy that raises the pressure from low pressure to high pressure by recovering it, it is possible to reduce the cost and improve energy performance.

Description

Refrigeration system {refrigeration system}

The present invention relates to a refrigeration system, and in particular, since the mutual energy is the same from high pressure to low pressure to low pressure to high pressure, using this to improve the performance and energy saving of the refrigerator using a refrigerant circulation device pressure loss from high pressure to low pressure By using the refrigerant circulation system that exchanges the mutual energy that raises the pressure from low pressure to high pressure by recovering it, it is possible to reduce the cost and improve energy performance.

In general, the freezing method in the refrigerator is divided into a natural freezing method using a natural external temperature and an artificial freezing method. The present invention is limited to an artificial freezing method.

The artificial refrigeration method is a method of obtaining a low temperature by expanding the compressed air, the absorption refrigeration apparatus using an absorbent is a general vapor compression refrigeration method using the heat of vaporization when the refrigerant vapor is condensed into the liquid phase and expanded into a gas.

However, the disadvantage of compressed refrigerators is that they require a lot of power. Even if you try to operate the air conditioner at home during the summer season, a 1-3 horsepower motor is built in to cool the refrigerant gas by returning it to the compressor. The refrigeration unit requires a large compressor drive power.

Therefore, the whole world is forced to build many power plants to develop civilization and pursue ideal life, and to freeze at night with low power consumption to cool during heavy loads, or to assist and finance low-power absorption refrigeration units. He is sympathetic to the power situation and the pursuit of civilization.

Therefore, the present inventors use all the apparatuses such as heat pump-cooling and heating devices, such as a refrigerating device or a cooling device air-conditioning device, with a small amount of electric power or a small amount of power, and all the devices as described above. If you continue to use it, the whole world must be covered by power plants.

In general, a compressor compresses a gas of low temperature and low pressure to a condensation pressure, and at a low pressure, a pressure is lowered to a vapor pressure at a low temperature and low pressure through a capillary tube or an expansion valve.

Since the pressure drops naturally from low pressure to high pressure, and from high pressure to low pressure, that is, most of the power used in the refrigerator when the pressure rises unilaterally is used for this pressure increase. In the refrigerating device, a large amount of external power is required. On the contrary, when the pressure drops from high temperature to high pressure to low pressure, the pressure drops naturally to the expansion valve or capillary tube, so the pressure from the high pressure to the low pressure is discarded. This is what happened.

Therefore, the present invention is the same as the energy energy of the pressure drop from high pressure to low pressure and the power energy of pressure rise from low pressure to high pressure, so if the recovery energy from the high pressure to low pressure, the amount of mutual energy is the same, The compression power of the compressor in the refrigerating device becomes unnecessary.

However, the freezer does not operate on simple principles or devices as we think it is, and does not consist only of simple pressures of high and low pressures. It is also called a heat pump that carries heat, and when the refrigerant circulates inside the device, it passes through a long coil and various devices, causing the passage resistance of the fluid, that is, the perfusion resistance, and the frictional loss and heat loss of the rotating part even in a high-low energy exchange device. In the real refrigeration system, such as a decrease in volume efficiency, to compensate for these losses, if the supplementary motor is provided by supplementing the losses to the external compressor or the rotating shaft of the energy exchanger of the high and low pressure, the invention can be used. The energy of the large power motor of the motor is not necessary.

If the present invention is commercialized and commercialized, a cold / hot water unit or a cold low temperature unit of a conventional water or ammonia lithium bromide absorption refrigerator (absorption refrigerator uses water or ammonia, which is a refrigerant gas evaporated from an evaporator using an absorbent property of water or lithium bromide). The refrigerant gas, which is absorbed and heated and separated again, is condensed by dissipating heat in the condenser and the condensed liquid is evaporated again in the evaporator. Since only a small amount of power energy is consumed in the circulation pump that circulates the refrigerant liquid without water, the government or environmental organization strongly recommends this. However, in the case of absorption type, if it is installed alone and operated without using waste heat of the power plant as heating heat source, Heating energy This will also eliminate the use of refrigeration and cooling systems, which are recommended in the future, and will reduce the speed and fuel consumption of the vehicle's engine load and reduce the fuel consumption. It is expected that there will be no power emergency due to the use of summer air conditioners, and the government's support for ice storage will be lost.

In addition, when the commercialization of the refrigeration system of the present invention starts, the world, including Korea, do not need to construct any more power plants, and use the refrigeration apparatus of the present invention instead of the boiler for heating in winter to absorb the heat of the outside air and move to the room. The air conditioning equipment of the heating low-power heat pump is put to practical use, and there is no expectation of the stocking of energy (imported oil) in winter.

Hereinafter, a conventional refrigeration system will be described.

The conventional refrigeration system, as shown in Figure 1, the compressor (10 ') for compressing the refrigerant gas to a condensation pressure in a state of high temperature and high pressure, and the refrigerant compressed by the compressor (10') cooling fan (10a ') Condenser 12 'condensed into liquid phase by heat dissipation by blowing air (in the case of water-cooled water, not water, other coolant or equipment is used and is described as air), and condensation in the condenser 12' An expansion valve 24 'for expanding the high temperature and high pressure liquid refrigerant into low-temperature gas phase refrigerant by throttling, and a blower using the latent heat of evaporation of the refrigerant while evaporating the expanded refrigerant at the expansion valve 24'. (26a ') (There are many types of evaporators depending on the type and structure of liquid, milk or other refrigeration system depending on the object to be cooled, but here, the description is air.) One Evaporator 26 'for returning the refrigerant gas to 0') consists of a refrigerant circulation cycle.

On the other hand, during the refrigeration cycle, the state must be changed from gas to liquid and liquid to gas continuously. If moisture is contained in the refrigerant, the water circulates in the apparatus together with the refrigerant during the freezing process, and water is frozen at low temperature parts such as expansion valves or capillaries. Because of the freezing and closing phenomenon that blocks the circulation circuit of the refrigerant, the freezing window stops and the phase change of the refrigerant is not made smoothly. (The freezer using ammonia is diluted with ammonia water when water penetrates. There is no accident, but the water evaporation pressure increases when water dilution, so water separation is necessary.) The refrigeration system is not able to function well and the refrigeration system is corroded. In particular, in a refrigeration system using a refrigerant such as R-12, when moisture is mixed with the refrigerant, the chemical reaction with the refrigerant shortens the life of the refrigerant due to corrosion resistance to the metal and reduces the life of the refrigerant. In the freezer, it will be fatally adversely affected.

In order to solve this problem caused by moisture, in the freezing incubator, a dryer 18 'that adsorbs moisture mixed in the refrigerant (adsorbent of porous material such as silica gel) is provided between the condenser 12' and the expansion valve 24 '. And a receiver 15 'for supplying only the liquid refrigerant to the expansion valve 24' between the condenser 12 'and the dryer 18'. That is, a desiccant and a filter are built into the housing of the dryer 18 'so that moisture is absorbed from the refrigerant flowing from the condenser 12' to the expansion valve 24 'by the desiccant, and the filter is applied to the refrigerant. Foreign matter other than moisture contained is filtered. In addition, the receiver 15 'temporarily stores the refrigerant in response to the load change of the refrigeration cycle, and separates the uncondensed refrigerant or the non-condensable gas contained in the liquid refrigerant, and also has a soluble plug. When installed, this fusible field is used to protect the system by forcibly discharging the refrigerant when the refrigerant is overheated beyond the refrigeration system.

On the other hand, when the refrigerant gas discharged from the evaporator 26 'is not completely evaporated, the refrigerant gas discharged contains liquid refrigerant, and when the refrigeration system is stopped, the evaporator 26' and the compressor 10 ' The refrigerant gas present in the conduit between turns into liquid phase. Therefore, the liquid refrigerant may flow into the compressor 10 ′. Since the liquid refrigerant is an incompressible fluid, when the liquid refrigerant flows into the compressor 10 ', a liquid compression phenomenon occurs and a hammer tapping noise, that is, a hammering noise is generated, and the liquid refrigerant is not compressed. ') Causes burnout.

Therefore, the necessity of fundamentally blocking the introduction of the liquid refrigerant into the compressor 10 'is required. For this purpose, the liquid refrigerant is separated between the evaporator 26' and the compressor 10 'and only the refrigerant gas is supplied to the compressor. A liquid separator 29 'is installed. In addition, a filter 32 'is provided between the liquid separator 26' and the compressor 10 'in order to prevent foreign matter from entering the compressor 10' and damage the compressor 10 '. Is installed more. Reference numeral 16 'of FIG. 1 denotes a solenoid valve for shutting off the refrigerant, and reference numeral 22' denotes a sight glasses.

However, in the conventional refrigeration system as described above, when the refrigerant passes through the receiver 16 ', the dryer 18' and the solenoid valve 16 ', the passage resistance is large and the capacity of the expansion valve 24' is increased. When the refrigerant passes through the receiver 15 'due to control or the like, it is in a full liquid state, but just before the expansion valve 24', the high pressure fluctuation is severe because the fluid flows while being crossed in a full liquid state and a half full liquid state. In order to prevent this, the refrigerant is always kept in a full state more than necessary in the receiver 15 ', but in this case, the size of the receiver 15' is increased and the amount of refrigerant is increased. Since the amount of use of the Freon refrigerant is limited after the Convention on the Restriction of the Use of the Freon Refrigerant which destroys the refrigerant, it is necessary to develop a freezer having a small amount of the Freon charge. In addition, in the conventional refrigeration system, the evaporator 26 'and the compressor 10 The liquid separator 29 'installed between') has a structure in which the liquid separation pipe installed inside the housing is bent in a U-shape so that the liquid refrigerant does not flow into the liquid separation pipe. Refrigerant and oil contained in the liquid refrigerant cannot be separated at the start of charging and low temperature, but flow into the compressor together with the liquid refrigerant. If the flow rate of the refrigerant gas flowing due to the rapid evaporation pressure fluctuation on the evaporator side is large, there is a high possibility that the liquid refrigerant will be attracted to the liquid separation pipe by the flow rate of the refrigerant gas and the use of the refrigerant refrigerant Unlimited freezing technology has been regarded as the basic technology.

The purpose of the present invention is simple structure, very small amount of power, and waste energy after operation (in the case of absorption type air conditioner or freezer, the boiler is heated more than necessary condensation heat dissipation. Condensation heat dissipation, such as heat generation of the motor equivalent heat of evaporation latent heat + compressor heat dissipation more than necessary, but the present invention the heat dissipation amount of the compressor only the lack of efficiency of the device, so the heat dissipation amount is less than the evaporation latent heat It doesn't increase much), it is cheaper than the current compression refrigeration unit, it is extremely low in price than the absorption refrigeration unit, and it can be applied to the conventional technology rather than the new theoretical technology.

It is a device for improving the performance of a refrigerator using a refrigerant circulation device using high and low pressure as described above. It recovers the lost pressure energy from high pressure to low pressure and raises the pressure from low pressure to high pressure. As the pressure of expansion valve, capillary tube, etc. drops, the pressure from high pressure to low pressure is discarded, which causes a large loss of power in the freezer.

Therefore, in the present invention, since the power energy of the pressure drop from the high pressure to the low pressure and the power energy of the pressure rise from the low pressure to the high pressure are the same, if the recovery energy from the high pressure to the low pressure is recovered, the amount of mutual energy is the same. If so, the compression power of the compressor in the refrigeration unit is unnecessary.

However, the freezer does not operate on simple principles or devices as we think it is, and does not consist only of simple pressures of high and low pressures. It is also called a heat pump that carries heat, and when the refrigerant circulates inside the device, it passes through a long coil and various devices, causing the passage resistance of the fluid, that is, the through-flow resistance, and the frictional loss and heat loss of the rotating part even in a high-low energy exchange device. In the real refrigeration system, such as a decrease in volumetric efficiency, to compensate for these losses, if a supplementary motor is installed on the rotating shaft of an auxiliary compressor or a high and low pressure energy exchanger to compensate for the loss, the large power in the current refrigeration system Refrigerant circulation to replace or replace the energy of the motor Value can be reduced to improve performance and reduce costs by using energy.

In order to achieve the above object, a refrigeration system according to the present invention, a compressor for compressing and discharging the refrigerant gas at a high temperature and high pressure state, a condenser for condensing the refrigerant compressed by the compressor in the liquid phase by heat dissipation, from the condenser A dryer for removing moisture contained in the discharged refrigerant, an expansion valve for expanding the liquid refrigerant in a high temperature and high pressure state condensed in the condenser, into a liquid refrigerant in a low pressure state by throttling action, and evaporating the refrigerant expanded in the expansion valve. While using a latent heat of evaporation of the refrigerant to achieve a refrigeration effect by heat exchange with the object to be cooled, an evaporator which evaporates and returns the refrigerant gas of low temperature and low pressure to the compressor, and a refrigerant gas discharged from the evaporator and returned to the compressor. It comprises a liquid separator for separating the liquid refrigerant fraction of the unevaporated liquid contained in Claims [1] A refrigeration apparatus system comprising: a pressure rising pump connected to an outlet end of the evaporator to suck a low temperature low pressure refrigerant gas and discharge the refrigerant gas into a high pressure refrigerant gas; It is characterized in that it comprises a refrigerant expansion pump connected to the outlet end of the dryer for discharging the sucked refrigerant to the evaporator.

The pressure raising pump and the refrigerant expansion pump may be installed coaxially, but each of them may be installed on a shaft other than the coaxial to have the same rotation by a transmission means such as a pulley.

The pressure raising pump and the refrigerant expansion pump is installed on the coaxial one more pressure raising pump is characterized in that the two-stage compression.

An intermediate cooler is further installed between the two pressure boost pumps.

The coaxial is characterized in that the motor further installed.

The cooling water supplied to the condenser has a first cooling inlet and a first cooling outlet so as to circulate primarily in a section corresponding to an isothermal and isobar on the condensation calorific value pi diagram of the condenser, and the cooling water discharged through the first cooling outlet. And a second coolant inlet and a second coolant outlet so as to circulate a part of the second condenser in the superheat removal section on the condensation calorific value pi diagram of the condenser again.

The evaporator is characterized in that the flow path through which the gas can pass between the two plates after spot welding as a whole.

An ejector for connecting the bypass line of the compressor to the discharge line of the compressor and the discharge line of the condenser, respectively, by the solenoid valve to the inlet end and connected to the outlet of the evaporator to recover the refrigerant by venturi action; And an outer housing connected to the outlet end of the dryer and connected to the inlet end of the expansion valve around the outlet end of the ejector side of the ejector.

The features and advantages of the present invention will become more apparent from the following detailed description of the preferred embodiments based on the accompanying drawings. Prior to this, the terms or words used in this specification and claims should not be construed as being limited to the ordinary or dictionary meanings, and the inventors may properly interpret the concept of terms in order to best explain their own invention. Based on the principle that can be defined, it should be interpreted as meaning and concept corresponding to the technical idea of the present invention.

<Example 1>

A refrigeration system according to Embodiment 1 of the present invention will be described with reference to FIG. 2.

Reference numeral 10 denotes a compressor which sucks refrigerant gas and compresses it at high temperature and high pressure and discharges it, and according to the purpose of use, various types of compressors such as reciprocating, crank, swash plate, wobble plate, rotary, scroll, etc. May be employed.

The discharge line of the compressor 10 is connected to the condenser 12, and the condenser 12 is condensed into a liquid refrigerant of high temperature and high pressure by radiating the refrigerant gas compressed and discharged from the compressor 10. Although not specifically illustrated here, the condenser 12 includes a plurality of tubes forming a predetermined flow path by connecting the upper header, the lower header, and the upper / lower headers to communicate with each other, and between the tubes. Conventional forms with corrugated heating fins stacked may be used. Therefore, the air blown by the cooling fan 14 passes through the heat transfer fins between the tubes, and in this process, the temperature of the refrigerant flowing in the condenser 12 is lost to the blower air, thereby performing the condensation of the refrigerant.

According to the present embodiment, the solenoid valve 16 for disconnecting the condensation refrigerant discharged from the condenser 12 through the receiver 15 is connected to the discharge line side of the condenser 12, the solenoid valve 16 On the discharge line side of the) is provided a dryer 18 for removing the water contained in the condensation refrigerant discharged from the condenser 12. The dryer 18 may be a conventional type in which a desiccant and a filter are built into the housing.

Therefore, moisture may be absorbed from the refrigerant flowing from the condenser 12 to the evaporator by the drying agent, and foreign matter other than the moisture contained in the refrigerant may be filtered by the filter.

On the other hand, the inlet line side of the compressor 10 by evaporating the refrigerant flowing from the expansion valve 24 to be described later by using the latent heat of evaporation at this time evaporator 26 to achieve a refrigeration effect by heat-exchanging the object and the refrigerant to be cooled ) Is connected, and the liquid separator 29 separating the liquid refrigerant contained in the refrigerant gas discharged from the evaporator 26 and returning only the refrigerant gas to the compressor 10 between the evaporator 26 and the compressor 10. ) Is installed, and a filter 32 is installed between the liquid separator 29 and the compressor 10 to remove foreign substances to prevent damage to the compressor 10 due to the inflow of foreign substances into the compressor 10. .

In addition, an expansion valve 24 for supplying the liquid refrigerant in the high temperature and high pressure state supplied to the inlet end of the evaporator 26 to the evaporator 26 so as to easily evaporate by expanding the liquid refrigerant in the low pressure state by the throttling action. Is installed. Although not shown in detail, the expansion valve 24 has an internal pressure equalization capillary tube for controlling the opening degree of the high-pressure refrigerant flow path through the pressure transfer rod by the expansion displacement of the diaphragm according to the temperature inside the thermostat chamber. The thermostatic expansion valve, generally called TEV, is used, such as external pressure control to control the opening degree of the high pressure refrigerant flow path by the expansion displacement of the diaphragm.

According to this embodiment, a receiver 15 for storing and discharging the high temperature and high pressure liquid refrigerant condensed by the condenser 12 is further installed in the conduit between the condenser 12 and the dryer 18. . In the case of the present embodiment, the receiver 15 may have a smaller capacity than the conventional one, and the receiver 15 may be removed.

According to this embodiment, bypass pipes 17a and 17b are provided in the discharge line of the compressor 10 and the discharge line of the condenser 12, respectively, and the bypass pipes 17a and 17b are It is connected to the inlet side of the ejector 27 and the outlet of the ejector 27 is connected to the filter 32. Then, the bypass pipes (17a) and (17b), respectively, to install and control the solenoid valves (13a) (13b). In addition, the present embodiment is to supply the refrigerant discharged from the evaporator 26 to the ejector 32 to recover the refrigerant of the evaporator in the venturi action during operation and to reverse the reverse direction 23 for preventing the reverse circulation to the evaporator Install.

Unexplained reference numeral 22 in Fig. 1 is a sight glasses, that is, the sight glass.

Next, the operation of the refrigeration system according to the present embodiment will be described.

When the compressor 10 is driven, the low pressure refrigerant gas discharged from the evaporator 26 and passed through the liquid separator 29 and the filter 32 is sucked into the compressor 10, and thus the refrigerant gas sucked into the compressor 10. Is compressed into a refrigerant gas of high temperature and high pressure and discharged to the condenser 12. The refrigerant gas introduced into the condenser 12 is radiated and condensed into a liquid refrigerant having a high temperature and high pressure, and flows into the dryer 18 through the solenoid valve 16. As the liquid refrigerant passes through the dryer 18, moisture and foreign substances contained in the liquid refrigerant are removed.

According to this embodiment, by measuring the pressure and temperature of the hot gas passed through the condenser 12 and the refrigerant discharged from the compressor 10 to control the solenoid valve 13a (13b) to supply to the ejector 27 By injecting, the inlet specific volume of the compressor 10 is reduced and the pressure is compensated for, thereby improving performance and reducing compression power. This embodiment recovers the refrigerant in the evaporator by venturi action during operation and prevents the reverse circulation to the evaporator by the reverse variable (23).

According to the present embodiment, the refrigerant flow rate and the hot gas can be controlled by the control valves 13a and 13b when the pressure of the evaporator decreases and the condensation pressure rises, thereby improving the refrigerating capacity and reducing the power required by the compressor. It can be attached to refrigeration equipment such as heat pump to improve performance and save power energy.

<Example 2>

A refrigeration system according to a second embodiment of the present invention will be described with reference to FIG. 3. In the present embodiment, the same reference numerals as those in the first embodiment refer to the same elements, and detailed descriptions of the same elements are omitted.

According to the present embodiment, an outer housing 30 connected to the outlet end of the dryer 18 and the inlet end of the expansion valve 24 is further installed around the outlet end pipe housing 27a of the ejector 27. The high temperature and high pressure liquid refrigerant discharged from the dryer 18 flows to the expansion valve 24 through a space between the outer surface of the housing 27a of the ejector 27 and the inner surface of the outer housing 30.

Therefore, the temperature of the high-temperature, high-pressure liquid refrigerant flowing through the space between the outer surface of the housing 27a of the ejector 27 and the inner surface of the outer housing 30 to the expansion valve 24 is discharged from the dryer 18. The liquid refrigerant contained in the refrigerant gas is completely vaporized by being transferred to the low pressure refrigerant gas discharged from the 26 and passing through the inside of the housing 27a of the ejector 27, thereby completely vaporizing the compressor 10 through the filter 32. Since the liquid refrigerant is not introduced into the compressor 10, the liquid compression of the compressor 10 is prevented. In addition, the liquid refrigerant deprived of the temperature in the refrigerant gas is lowered in temperature and flows into the evaporator 26 through the expansion valve 24 in a state in which the refrigerant gas that can be contained in the liquid refrigerant is condensed, the latent heat of evaporation increases and the freezing performance is increased Can be improved.

In the refrigerant cycle process, the high-temperature, high-pressure liquid phase is discharged from the dryer 18 and flows to the expansion valve 24 through a space between the outer surface of the housing 27a of the ejector 27 and the inner surface of the outer housing 30. The coolant comes into contact with the outer surface of the housing 27a of the ejector 27. Accordingly, the temperature of the liquid refrigerant is discharged from the evaporator 26 to heat transfer to the low pressure refrigerant gas passing through the housing 27a of the ejector 27 to heat the refrigerant gas. Therefore, since the liquid refrigerant contained in the refrigerant gas is completely vaporized and supplied to the compressor 10 through the filter 32, the liquid refrigerant of the compressor 10 is prevented as the liquid refrigerant does not flow into the compressor 10. can do. On the contrary, the liquid refrigerant whose temperature has been deprived of the refrigerant gas is introduced into the evaporator 26 through the expansion valve 24 while the temperature of the liquid refrigerant is lowered and the refrigerant gas which may be contained in the liquid refrigerant is condensed. Freezing performance can be improved.

<Example 3>

A refrigeration system according to a third embodiment of the present invention will be described with reference to FIG. 4. Also in the present embodiment, the same reference numerals as the above embodiments indicate the same elements, and detailed descriptions of the same elements are omitted.

According to the present embodiment, the refrigerant expansion pump 25 and the pressure raising pump 11 are installed in the configuration of the second embodiment. The compressor 10 serves as an auxiliary compressor here. Since the refrigerant gas from the evaporator of low temperature and low pressure is sucked into the inlet of the pressure raising pump 11, and the outlet of the pressure raising pump 11 is discharged from the refrigerant gas of high temperature and high pressure, this corresponds to a compressor. Therefore, the compressor 10 according to the second and third embodiments is an auxiliary compressor.

In addition, the high pressure liquid refrigerant flows into the inlet of the refrigerant expansion pump 25 and the outlet flows into the liquid refrigerant of low temperature and low pressure, while the kinetic energy caused by the pressure difference from the high pressure to the low pressure rotates on the same shaft. Therefore, since the kinetic energy of both the refrigerant expansion pump 25 and the pressure raising pump 11 is the same, no external power is required to rotate the pump. However, in a real refrigeration system, frictional losses of the rotating part, refrigerant condenser or evaporator, etc. The auxiliary compressor should compensate for the loss and resistance due to the perfusion resistance such as the pass resistance of other equipment, and the control of this auxiliary compressor can control the operation under the condition of the user's desired temperature. Control is possible.

According to the present embodiment, the refrigerant expansion pump 25 and the pressure gas pump 11 may circulate the refrigerant using mutual energy from low pressure to high pressure from high pressure to low pressure. The refrigerant pump method may be a vane, a piston, a scroll, a gear, a diaphragm, a bellows, a rotary volume method or a rotary turbo type.

<Example 4>

A refrigeration system according to a fourth embodiment of the present invention will be described with reference to FIG. 5. Also in the present embodiment, the same reference numerals as the above embodiments indicate the same elements, and detailed descriptions of the same elements are omitted.

According to the present embodiment, in the third embodiment, the auxiliary compressor is excluded and the motor 9 is installed on the coaxial 11b of the refrigerant expansion pump 25 and the pressure raising pump 11. In this embodiment, no auxiliary compressor is required. The motor 9 is installed on the coaxial 11b of the refrigerant expansion pump 25 and the pressure raising pump 11 by the energy lost due to frictional loss such as friction loss or through resistance of the refrigerant, such as a condenser or evaporator of the refrigerant. Loss compensation and operational control can simplify equipment and reduce production costs.

As such, the power required when the pressure rises from the low pressure to the condensation pressure is operated by the energy of the refrigerant expansion valve 24 from the condensation pressure to the evaporation pressure, thereby improving the performance of the refrigerating device as well as reducing the operating power energy.

When the refrigeration unit is operated as described above, when the compressor is compressed only by the compressor, the life of the refrigerator or the heat of condensation are increased due to the heat generated by the compressor and the heat generated by the adiabatic compression of the refrigerant, but the energy saving and the life of the machine can be extended by using the apparatus of the present invention. do.

As the mutual energy is the same from low to high pressure from high pressure to low pressure, it is a device for improving the performance and energy saving of the refrigerator using the refrigerant circulation device, and recovering the lost pressure energy from high pressure to low pressure to increase the pressure from low pressure to high pressure. The state can improve the performance and reduce the energy by using the refrigerant circulation system that exchanges energy with each other.

<Example 5>

A refrigeration system according to a fifth embodiment of the present invention will be described with reference to FIG. 6. Also in the present embodiment, the same reference numerals as the above embodiments indicate the same elements, and detailed descriptions of the same elements are omitted.

According to this embodiment, the receiver is removed in the fourth embodiment, the liquid receiver is heat exchanged with the refrigerant gas passing through the liquid separator 29 through the liquid refrigerant passing through the outer housing 30 of the outlet end side of the ejector and then expansion valve ( 24, the receiver 15 may be removed in the present embodiment.

<Example 6>

A refrigeration system according to a sixth embodiment of the present invention will be described with reference to FIG. 7. Also in the present embodiment, the same reference numerals as the above embodiments indicate the same elements, and detailed descriptions of the same elements are omitted.

According to the present embodiment, a low-pressure pump 11a is applied to the coaxial 11b of the refrigerant expansion pump 25 and the pressure phase pump 11 of the above embodiments as a two-stage compression cycle using an ejector at a low temperature. It is a more equipped configuration.

<Example 7>

A refrigeration system according to a seventh embodiment of the present invention will be described with reference to FIG. 8. In the present embodiment, the same reference numerals as those in the sixth embodiment indicate the same elements, and detailed descriptions of the same elements are omitted.

According to this embodiment, the intermediate cooler 28 is further provided in the sixth embodiment. The intermediate cooler 28 is installed between the two pressure raising pumps 11 and 11a to improve performance, and the inlet end side of the intermediate cooler 28 is connected to the pressure raising pump 11. The outlet end side of the intermediate cooler 28 is connected to another pressure raising pump 11a.

Thus, the present embodiment can be expected to improve the performance of the refrigeration cycle as the refrigerant through the pressure increase pump 11 is introduced into the pressure gas pump (11a) after passing through the intermediate cooler (28).

<Example 8>

A refrigeration system according to Embodiment 8 of the present invention will be described with reference to FIG. 9. Also in the present embodiment, the same reference numerals as the above embodiments indicate the same elements, and detailed descriptions of the same elements are omitted.

According to this embodiment, the receiver is removed in Example 7 above. Since the liquid receiver flows to the expansion valve 24 after the liquid refrigerant passing through the outlet-side pipe outer housing 30 of the ejector is exchanged with the refrigerant gas passing through the liquid separator 29, the receiver 15 in the present embodiment May be removed.

Example 9

A refrigeration system according to a ninth embodiment of the present invention will be described with reference to FIGS. 10 and 11. Also in the present embodiment, the same reference numerals as the above embodiments indicate the same elements, and detailed descriptions of the same elements are omitted.

According to the present embodiment, in the above embodiments, to improve the condensate (cooling water) and the evaporator to improve the freezing to bring about the effect of improving efficiency and reducing the refrigerant charge amount, the cooling water supplied to the condenser 12 The cycle of is different.

The cooling water is supplied through the first cooling inlet 12a to be discharged to the first cooling outlet 12b. Since the amount of cooling water of the first cooling outlet 12b in the first cooling inlet 12a corresponds to an isothermal and isobar on the condensation calorific value pi diagram of the condenser shown in FIG. 11, it corresponds to the pure condensation calorific value.

In addition, a part of the cooling water discharged to the first cooling outlet 12b is supplied through the second cooling inlet 12c to be discharged to the second cooling outlet 12d. The amount of heat of cooling water of the second cooling outlet 12d at the second cooling inlet 12c is the amount of heat of the superheat removal section on the condensation calorific value pi diagram of the condenser shown in FIG. 11, and the first supercooling section is less than the amount of condensation heating. Re-injecting part of the cooling water discharged through the outlet 12b lowers the condensation pressure, decreases the capacity of the condenser, consequently increases the efficiency, and shortens the condensation line, thereby reducing the refrigerant charge amount.

According to this embodiment, if the temperature of the first cooling inlet 12a is approximately 30 ° C, the temperature of the first cooling outlet 12b is approximately 45 ° C. Therefore, the temperature of the second cooling inlet 12c may be approximately 45 ° C., and the temperature of the second cooling outlet 12d may be approximately 70 ° C.

In addition, since the conventional evaporator uses a long pipe for the refrigerant pipe, the efficiency of the pipe decreases due to the increase in the perfusion resistance of the pipe and the amount of refrigerant remaining in the inner pipe. However, according to the present embodiment, the evaporator plate uses two evaporator plates. After spot welding 16 ′ of the plate 26a as a whole, a flow path 26b through which gas can pass is formed and the refrigerant gas passes between the two plates 26a to shorten the total distance of the refrigerant gas. Since the refrigerant gas flows to the plate widely, the resistance of the refrigerant gas in the plate is low and the content is smaller than that of the pipe, so it is economically efficient and the amount of refrigerant charged can be reduced.

In the method for manufacturing an evaporation plate according to the embodiment, the two plates (26a) are overlapped, and two sheets are joined by spot seam welding (26 ') at regular intervals, and then the size of the refrigeration system for the flow and spread of the refrigerant. Depending on the type, the flow path 26b is removed or multiplely installed to weld the surroundings, and the air or Co2 is pressurized between the two plates 26a, that is, by pressurizing with gas or hydraulic pressure, so as to separate the two flow channels 26b. Allow a suitable gap to be formed and allow the refrigerant gas to flow between the formed gaps.

12A and 12B, the evaporator plate forms the flow path 26b in various shapes according to the size or shape of the container to serve as the evaporator of the refrigerator.

13 and 14 illustrate control states of the refrigeration system according to the exemplary embodiments described above.

13 and 14, there is a difference that the auxiliary compressor 10 is installed in the refrigeration system, it will be described at the same time. 13 and 14, an electronic controller 40 for controlling a refrigeration system according to the present invention is provided. The electronic controller 40 calculates values input from various sensors and adjusts the rotational speed of the motor by analog, digital, and phase hertz control so that the user operates under a desired condition.

As the various signals input to the electronic controller 40, first, moisture detection of the refrigerant flowing into the refrigerant expansion pump 25, condensation pressure detection at the discharge port side of the condenser 12, evaporation pressure detection of the evaporator 26, The pressure reduction side density detection of the refrigerant expansion pump 25 and the pressure increase side density detection of the pump 11 for increasing the pressure.

In addition, the electronic controller 40 adjusts the mutual volume balance between the refrigerant expansion pump 25 and the pressure raising pump 11, and controls on / off of the auxiliary compressor 10 and the motor 9. The electronic controller 40 is connected to the outdoor temperature sensor 42 and the high temperature sensor 44 to control the electronic controller 40.

According to the present invention, in a refrigerating device in which the compression ratio is changed depending on an operation state such as a low temperature freezer, the temperature of the discharged gas of the compressor is rapidly increased when the compression ratio is increased, and when the condensation pressure is increased, the volume efficiency and the compression efficiency are increased rapidly. In addition, the present invention, as apparent from the above description in order to compensate for the damage of the compressor, such as a sudden shortening of the life of the compressor by overheating of the compressor and deterioration and carbonization of the lubricant of the rotary slip compressor of the motor for driving the compressor. Refrigerant flow rate and hot gas control in case of lowering and condensation pressure, improving the refrigerating capacity and reducing the power consumption of the compressor, and attaching it to existing refrigerators such as refrigerators, air conditioners and heat pumps to improve performance and reduce power energy. There is.

1 is a block diagram showing a conventional refrigeration system

2 is a block diagram showing a refrigeration system according to a first embodiment of the present invention

3 is a configuration diagram showing a refrigeration system according to a second embodiment of the present invention

4 is a configuration diagram showing a refrigeration system according to a third embodiment of the present invention

5 is a configuration diagram showing a refrigeration system according to a fourth embodiment of the present invention

6 is a configuration diagram showing a refrigeration system according to a fifth embodiment of the present invention

7 is a configuration diagram showing a refrigeration system according to a sixth embodiment of the present invention

8 is a configuration diagram showing a refrigeration system according to a seventh embodiment of the present invention

9 is a configuration diagram showing a refrigeration system according to an eighth embodiment of the present invention

10 is a configuration diagram showing a refrigeration system according to a ninth embodiment of the present invention

FIG. 11 is a diagram showing pi of the condensation calorific value of the condenser according to Embodiment 9 of FIG. 10; FIG.

12a and 12b are views showing the evaporation plate of the evaporator according to the ninth embodiment of FIG. 10 in various shapes.

13 and 14 is a configuration diagram showing an electronic control state of the refrigeration system according to the present invention

<Explanation of symbols for the main parts of the drawings>

10-compressor 11-motor

11,11a-Pressure boosting pump 12-Condenser

13a, 13b-Solenoid valve 17a, 17b-bypass tube

18-Dryer 24-Expansion Valve

25-Refrigerant Expansion Pump 26-Evaporator

27-ejector 27a-housing

28-intermediate cooler 30-outer housing

32-filter

Claims (8)

A compressor for compressing and discharging the refrigerant gas at a high temperature and high pressure, a condenser for condensing the refrigerant compressed in the liquid phase by heat radiation, a dryer for removing moisture contained in the refrigerant discharged from the condenser, and condensing in the condenser An expansion valve for expanding a liquid refrigerant in a high temperature and high pressure state into a liquid refrigerant in a low pressure state by a throttling action, and using a latent heat of evaporation of the refrigerant while evaporating the refrigerant expanded in the expansion valve to effect a freezing effect by heat exchange with the object to be cooled. A refrigeration system comprising an evaporator for evaporating and returning a low-temperature, low-pressure gaseous refrigerant gas to a compressor, and a liquid separator for separating an unevaporated liquid refrigerant content contained in the refrigerant gas discharged from the evaporator and returned to the compressor. A pressure raising pump installed at an outlet side of the evaporator to inhale a low temperature low pressure refrigerant gas flowing from the evaporator and discharge the refrigerant gas into a high pressure refrigerant gas; And And a refrigerant expansion pump installed coaxially with the pressure raising pump and connected to an outlet end of the dryer to discharge the sucked refrigerant to an evaporator. delete The refrigeration system according to claim 1, wherein one more pressure boosting pump is installed at the coaxial between the pressure raising pump and the refrigerant expansion pump. The refrigeration system of claim 3, wherein an intermediate cooler is further installed between the two pressure boost pumps. The refrigeration system according to claim 3, wherein the coaxial shaft further includes a motor. The cooling water supplied to the condenser has a first cooling inlet and a first cooling outlet so as to circulate primarily in a section corresponding to an isothermal and isobar on the condensation calorific value pi diagram of the condenser. And a second coolant inlet and a second coolant outlet so that a part of the coolant discharged through the outlet is circulated again to the superheat removal section on the condensation calorific value pi diagram of the condenser. The refrigeration system according to claim 1, wherein the evaporator has a flow path through which spot gas is welded on two plates as a whole and gas can pass therebetween. The discharge line of the compressor and the discharge line of the condenser are respectively connected to the inlet end of the bypass line controlled by the solenoid valve, and the outlet end of the evaporator is connected to recover the refrigerant by venturi action. And an ejector, an outer housing connected to an outlet end of the dryer and connected to an inlet end of the expansion valve, around an outlet end pipe passage housing of the ejector.