JP5371660B2 - Compression refrigerator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compression type refrigerating machine which eliminates gaseous and liquid impurities from a plurality of refrigerating cycles such as a double refrigerating cycle or a plurality of compression-type refrigerating machines by one impurity elimination device for eliminating the gaseous and liquid impurities. <P>SOLUTION: In this compression type refrigerating machine including the plurality of refrigerating machines with refrigerating cycles, or the plurality of refrigerating cycles, is provided with an extraction gas moving means for extracting a refrigerant gas including the gaseous impurity from one of the refrigerating cycles and moving the same to the other refrigerating cycle, a refrigerant liquid moving means for moving the refrigerant liquid including the liquid impurity from the refrigerating cycle different from one of the refrigerating cycles, to the other refrigerating cycle of the direction opposite to the moving direction of the gas moved by the extraction gas moving means, an extraction device 33 disposed in the refrigerating cycle of the final stage for moving the gas by the extraction gas moving means, to extract the gaseous impurity, and discharge the same to outside a system, and a concentrating device 32 disposed in the refrigerating cycle of the final stage for moving the refrigerant liquid by the refrigerant liquid moving means, to extract the liquid impurity and discharge the same to outside the system. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to a compression refrigerator, and more particularly to a compression refrigerator that can efficiently eliminate impurities that have entered a refrigerant circulation path.

  FIG. 1 is a diagram showing a schematic configuration of a conventional compression refrigerator of this type. The compression refrigerator 100 includes an evaporator 101, a compressor 102, a condenser 103, and an expansion valve 104. The evaporator 101 takes away the heat of cold water (not shown) as a fluid to be cooled and evaporates the refrigerant. The refrigerant vapor is compressed by the compressor 102, and the compressed refrigerant vapor is cooled and condensed with cooling water by the condenser 103 to be liquefied, and the liquefied refrigerant is expanded via the expansion valve 104 to the evaporator 101. A refrigeration cycle that maintains the refrigeration action by returning it is configured.

  FIG. 2 is a diagram showing a schematic configuration of a conventional compression refrigerator of this type of double refrigeration cycle. The compression refrigerator 200 includes a low-pressure evaporator 201, a low-pressure compressor 202, a low-pressure condenser 203, a low-pressure expansion valve 204, a high-pressure evaporator 211, a high-pressure compressor 212, a high-pressure condenser 213, and A high-pressure side expansion valve 214 is provided.

  The refrigerant vapor evaporated by the low-pressure side evaporator 201 is compressed by the low-pressure side compressor 202, and the compressed refrigerant vapor is cooled and condensed by the low-pressure side condenser 203 to be liquefied, and the liquefied refrigerant is supplied to the low-pressure side expansion valve. A low-pressure side refrigeration cycle that maintains the refrigeration action by returning to the low-pressure side evaporator 201 via 204 is configured. Further, the refrigerant vapor evaporated by the high-pressure side evaporator 211 is compressed by the high-pressure side compressor 212, and the compressed refrigerant vapor is cooled and condensed by the high-pressure side condenser 213 to be liquefied. A high-pressure side refrigeration cycle that maintains the refrigeration action by returning to the high-pressure side evaporator 211 via the expansion valve 214 is configured.

  As described above, the compression refrigerator compresses the refrigerant vapor evaporated in the evaporator with the compressor, cools and condenses it with the condenser, and liquefies it, and returns it to the evaporator through the expansion valve to achieve the refrigeration action. It lasts. Here, when impurities are mixed in the refrigerant sealed in the refrigerant circulation path of the refrigeration cycle, the action of evaporation and condensation of the refrigerant is hindered, and the performance of the refrigerator is lowered.

  Impurities in the refrigerant are roughly classified into non-condensable gases and liquid impurities. Non-condensable gas impurities include nitrogen and oxygen contained in air and the like, and liquid impurities include moisture and lubricating oil for refrigerators. These impurities are slight airtight defects of the refrigerator, those mixed during the manufacturing of the refrigerator or the manufacturing process of the refrigerant, those that enter from the outside during the holding operation of the refrigerator, especially in the case of lubricating oil, What is circulating in the refrigerator for lubrication of the compressor is leaked into the refrigerant circuit.

  Conventionally, the non-condensable gas mixed in the refrigerant sealed in the refrigerant circulation path of the refrigerator is not condensed in the condenser and thus tends to stay as a gas, thereby inhibiting the condensing action. For this reason, the compression type refrigerator 100 shown in FIG. 1 is provided with an extraction device 105, and the compression type refrigerator 200 shown in FIG. 2 is provided with a low pressure side extraction device 205 and a high pressure side extraction device 215, and a condenser (condenser 103, low pressure side) is provided. The refrigerant 203 and the high-pressure side condenser 213) are led to the extraction device together with the refrigerant gas, and the refrigerant cooled by the cooler in the extraction device (extraction device 105, extraction device 205, extraction device 215) is cooled. Only the non-condensable gas that is returned to the evaporator (evaporator 101, low-pressure side evaporator 201, high-pressure side evaporator 211) and does not condense even when cooled is concentrated to a certain concentration and then outside the machine. Is discharged. At this time, the refrigerant gas contained in the exhaust gas may be further adsorbed by activated carbon or the like. In any case, the extraction of the non-condensable gas requires the extraction device 105, the low pressure side extraction device 205, the high pressure side extraction device 215, etc., and there is a problem that costs are increased.

  On the other hand, since liquid impurities are hard to evaporate, they are likely to stay in the evaporator, and the liquid impurities staying in the evaporator hinder the evaporation of the refrigerant. For this reason, various methods for recovering the accumulated impurities have been developed. For example, in the compression refrigerator 100 shown in FIG. 1, the concentrator 106 is provided in the evaporator 101, and in the compression refrigerator 200 shown in FIG. Concentrator 206 is provided in the vessel 201, and a concentrator 216 is provided in the high-pressure side evaporator 211, and impurities in the evaporator (evaporator 101, low-pressure side evaporator 201, high-pressure side evaporator 211) are concentrated by overheating. There is a way. In this case, most of the impurities are lubricating oil, and the recovered lubricating oil is also returned to the lubricating oil tank. In this case as well, recovery devices such as the concentrating device 106, the concentrating device 206, and the concentrating device 216 are necessary for recovering the impurities, which increases the cost of the refrigerator.

  These impurity recovery devices (bleeding devices and concentrating devices) are generally provided one by one for one refrigeration cycle. Therefore, in the case of a compression refrigeration unit of a normal single refrigeration cycle, one unit for the compression chiller On the other hand, a collection device (a bleeder or a concentrator) is provided one by one. Furthermore, if it was a refrigerator with a double refrigeration cycle, it was necessary to provide two units each.

  The present invention has been made in view of the above points, and is a single impurity removing device that removes gaseous and liquid impurities and gas from a plurality of refrigeration cycles such as a double refrigeration cycle, or a plurality of compression refrigerators. It is an object of the present invention to provide a compression refrigerator that can remove solid and liquid impurities.

In order to solve the above problems, the present invention includes an evaporator, a compressor, a condenser, and an expansion valve. The evaporator takes heat from the fluid to be cooled to evaporate the refrigerant, and the evaporated refrigerant vapor is removed. A plurality of refrigerators having a refrigeration cycle configured to compress by a compressor, cool the condensed refrigerant vapor with a cooling fluid by a condenser, condense, and expand the condensed refrigerant liquid through an expansion valve and return the refrigerant liquid to an evaporator Or, in a compression-type refrigerator having a plurality of refrigeration cycles, extraction gas moving means for extracting a refrigerant gas containing gaseous impurities from one refrigeration cycle and moving it to another refrigeration cycle, and gas extracted by the extraction gas moving means moves the extracted gas moving means and bleed system for discharging the gaseous impurities out of bled system in a refrigeration cycle of the final stage moving, the refrigerant liquid containing liquid impurities from another refrigeration cycle as one of the refrigeration cycle The liquid liquid moving means for moving to another refrigeration cycle in the direction opposite to the moving direction of the gas, and the liquid impurity extracted into the final refrigeration cycle for moving the refrigerant liquid by the refrigerant liquid moving means and discharged out of the system An impurity recovery means is provided .

  Further, according to the present invention, in the above-described compression refrigerator, the extraction gas moving means includes an extraction pipe for moving a refrigerant gas containing gas impurities extracted from one refrigeration cycle, and the flow rate of the gas flowing through the extraction pipe is reduced. A flow rate limiting means for limiting is provided.

  Further, the present invention is the above-described compression type refrigerator, wherein the refrigerant liquid moving means is a liquid impurity from the evaporator of the downstream refrigeration cycle of the gas moved by the extraction gas moving means to the evaporator of the one-stage upstream refrigeration cycle. And a control means for controlling the refrigerant liquid that moves through the refrigerant moving pipe.

  Further, the present invention is characterized in that, in the compression refrigerator, the liquid impurity collecting means is a concentrating device for extracting liquid impurities by concentrating the refrigerant liquid by overheating.

  Further, the present invention provides the above-described compression refrigerator, wherein the plurality of refrigeration cycles are a low-pressure refrigeration cycle and a high-pressure refrigeration cycle, and the extraction gas moving means is a refrigerant containing gaseous impurities from the condenser of the low-pressure refrigeration cycle. The gas is moved to the condenser of the high-pressure side refrigeration cycle.

  Further, the present invention is characterized in that in the above-described compression type refrigerator, the refrigerant liquid moving means moves the refrigerant liquid containing liquid impurities from the evaporator of the high pressure side refrigeration cycle to the evaporator of the low pressure side refrigeration cycle.

  The present invention relates to a compression type refrigerator having a plurality of refrigeration cycles, extraction gas moving means for extracting refrigerant gas containing gaseous impurities from one refrigeration cycle and moving it to another refrigeration cycle, and one refrigeration cycle Moves a refrigerant liquid containing liquid impurities from another refrigeration cycle to another refrigeration cycle in a direction opposite to the moving direction of the gas moving by the extraction gas moving means, and moves the gas by the extraction gas moving means A bleeder that bleeds gaseous impurities to the final stage refrigeration cycle and discharges them outside the system, and a concentrator that extracts liquid impurities to the last stage refrigeration cycle that moves the refrigerant liquid by the refrigerant liquid moving means and discharges it outside the system By providing one impurity removal device with one bleeder and one concentrator, multiple refrigeration cycles such as a double refrigeration cycle, or multiple refrigeration cycles It is possible to remove impurities from the condensed chiller can contribute to cost reduction.

FIG. 1 is a diagram showing a schematic configuration example of a conventional compression refrigerator. FIG. 2 is a diagram showing a schematic configuration example of a conventional compression refrigerator. FIG. 3 is a diagram showing a schematic configuration example of a compression refrigerator according to the present invention. FIG. 4 is a diagram showing a schematic configuration example of the compression refrigerator according to the present invention. FIG. 5 is a diagram showing a schematic configuration example of the compression refrigerator according to the present invention. FIG. 6 is a diagram showing a schematic configuration example of the compression refrigerator according to the present invention.

  Hereinafter, embodiments of the present invention will be described in detail. FIG. 3 is a diagram showing a schematic configuration example of a compression refrigerator according to the present invention. This compression refrigerator 10-1 is a compression refrigerator having two independent refrigeration cycles A and B. The refrigeration cycle A includes an evaporator 11-1, a compressor 12-1, a condenser 13-1, and an expansion valve 14-1. The refrigerant vapor evaporated by the evaporator 11-1 is compressed by the compressor 12-1. The refrigerant vapor is cooled and condensed by the condenser 13-1 to be liquefied, and the liquefied refrigerant is returned to the evaporator 11-1 through the expansion valve 14-1, thereby constituting a refrigeration cycle. Yes. The refrigeration cycle B includes an evaporator 11-2, a compressor 12-2, a condenser 13-2, and an expansion valve 14-2. The refrigerant vapor evaporated by the evaporator 11-2 is supplied to the compressor 12-2. The compressed refrigerant vapor is cooled and condensed by the condenser 13-2 to be liquefied, and the liquefied refrigerant is returned to the evaporator 11-1 through the expansion valve 14-2 to constitute a refrigeration cycle. doing.

  An extraction pipe L for extracting refrigerant gas from the condenser 13-1 of one refrigeration cycle A is connected to the evaporator 11-2 of the other refrigeration cycle B via an orifice 31. The non-condensable impurities in the condenser 13-1 of the refrigeration cycle A move to the evaporator 11-2 of the refrigeration cycle B together with the extracted refrigerant gas (refrigerant vapor). In the refrigeration cycle B, non-condensable impurities circulate together with the refrigerant, and finally accumulate in the condenser 13-2 of the refrigeration cycle B. The accumulated non-condensable impurities are discharged out of the system by the extraction device 33 provided in the refrigeration cycle B. The function of the bleeder 33 is the same as that of the bleeders 105, 205, and 215 shown in FIGS.

  The refrigerant amount gradually increases in the refrigeration cycle B due to the moving refrigerant. The amount of increase in the refrigerant can be detected by monitoring the refrigerant liquid level in the evaporator 11-2 and the refrigerant liquid level in the condenser 13-2. Here, by providing the overflow weir 22 on the side surface of the evaporator 11-2, when the refrigerant liquid level in the evaporator 11-2 rises, the refrigerant liquid overflowing the overflow weir 22 passes through the motor-operated valve 24. Is sent to the evaporator 11-1 and returned to the refrigeration cycle A. Here, the driving force necessary for the movement of the refrigerant is ensured by design such that the pressure of the refrigeration cycle B is higher than that of the refrigeration cycle A, or the kinetic energy of the refrigerant in the refrigerant pipe (so-called venturi mechanism or the like) ). Moreover, you may use an ejector, a pump, etc. as needed. At this time, the liquid impurities in the refrigeration cycle B move to the refrigeration cycle A together with the refrigerant liquid. The evaporator 11-1 of the refrigeration cycle A is provided with an impurity concentrating device 32, the refrigerant liquid level of the evaporator 11-1 is increased, and the flow weir 21 provided on the side surface of the evaporator 11-1. When the value exceeds, the overflowing refrigerant liquid moves to the concentrating device 32, whereby the impurities are recovered. The function of the concentrator 32 is the same as that of the concentrators 106, 206, and 216 shown in FIGS.

  In the above example, the extraction pipe L from the condenser 13-1 of one refrigeration cycle A is connected to the evaporator 11-2 of the refrigeration cycle B, and the refrigerant gas containing the impurity gas extracted from the condenser 13-1 Although it moved to the evaporator 11-2, the moving destination of the refrigerant gas containing the impurity gas is not limited to the evaporator 11-2 and is substantially lower than the condenser 13-1 of the refrigeration cycle A. What is necessary is just the location of the refrigerating cycle B where it is expected. Further, it is preferable to provide a flow restricting means such as an orifice in the extraction pipe. In addition, a bleeder is provided in the condenser 13-2 of the refrigeration cycle B that is the final end. By doing in this way, impurities can be simultaneously recovered from two independent refrigeration cycles A and B by one extraction device 33 and one concentration device 32.

  FIG. 4 is a diagram showing a schematic configuration example of the compression refrigerator according to the present invention. This compression refrigerator 10-2 is a double-cycle compression refrigerator having a low-pressure refrigeration cycle and a high-pressure refrigeration cycle. The compression refrigerator 10-2 includes a low pressure side evaporator 41, a low pressure side compressor 42, a low pressure side condenser 43, a low pressure side expansion valve 44, a high pressure side evaporator 51, a high pressure side compressor 52, a high pressure side condenser 53, A high-pressure side expansion valve 54 is provided.

  The refrigerant vapor evaporated by the low-pressure side evaporator 41 is compressed by the low-pressure side compressor 42, and the compressed refrigerant vapor is cooled and condensed by the low-pressure side condenser 43 to be liquefied, and the liquefied refrigerant is supplied to the low-pressure side expansion valve. The low pressure side refrigeration cycle is configured by returning to the low pressure side evaporator 41 via 44. The refrigerant vapor evaporated by the high pressure side evaporator 51 is compressed by the high pressure side compressor 52, and the compressed refrigerant vapor is cooled and condensed by the high pressure side condenser 53 to be liquefied, and the liquefied refrigerant is The high pressure side refrigeration cycle is configured by returning to the high pressure side evaporator 51 via the expansion valve 54. A concentrator 62 is provided in the low-pressure evaporator 41 of the low-pressure refrigeration cycle, and a bleeder 63 is provided in the high-pressure condenser 53 of the high-pressure refrigeration cycle.

  An extraction pipe L for extracting refrigerant gas from the condenser 43 of the low-pressure side refrigeration cycle is connected to the high-pressure side evaporator 51 of the high-pressure side refrigeration cycle via an orifice 61. Non-condensable impurities in the condenser 43 of the low-pressure side refrigeration cycle move to the high-pressure side evaporator 51 of the high-pressure side refrigeration cycle together with the extracted refrigerant gas (refrigerant vapor). In the high-pressure side refrigeration cycle, non-condensable impurities circulate together with the refrigerant, and finally accumulate in the high-pressure side condenser 53 of the high-pressure side refrigeration cycle. The accumulated non-condensable impurities are discharged out of the system by the extraction device 63 provided in the high-pressure side refrigeration cycle.

  Due to the moving refrigerant, the amount of refrigerant gradually increases in the high-pressure side refrigeration cycle. The increased amount of the refrigerant can be detected by monitoring the refrigerant liquid level in the high pressure side evaporator 51 and the refrigerant liquid level in the high pressure side condenser 53. Here, the liquid level of the low-pressure evaporator 41 is monitored by the liquid level detector 45, and when the refrigerant liquid level falls below a specified level, the automatic valve 64 is opened to reduce the refrigerant liquid from the high-pressure evaporator 51 to low pressure. Move to side evaporator 41. Here, the driving force necessary for the movement of the refrigerant is ensured by design such that the pressure of the high-pressure side refrigeration cycle is higher than that of the low-pressure side refrigeration cycle, or the kinetic energy of the refrigerant in the refrigerant pipe (so-called venturi mechanism) Etc.). Moreover, you may use an ejector, a pump, etc. as needed.

  As described above, by moving the refrigerant liquid from the high pressure side evaporator 51 to the low pressure side evaporator 41, the liquid impurities in the high pressure side refrigeration cycle move to the low pressure side refrigeration cycle together with the refrigerant liquid. When the refrigerant liquid level of the low-pressure side evaporator 41 rises and exceeds the overflow weir 46 provided on the side surface of the low-pressure side evaporator 41, the overflowing refrigerant liquid moves to the concentrator 62, whereby the impurities are recovered. . In this way, by providing one impurity removal device comprising one extraction device 63 and one concentration device 62 in the double cycle compression refrigerator 10-2, the low pressure side refrigeration cycle and the high pressure side are provided. Impurities can be recovered simultaneously from the refrigeration cycle.

  FIG. 5 is a diagram showing a schematic configuration example of the compression refrigerator according to the present invention. This compression refrigerator 10-3 is a compression refrigerator having three independent refrigeration cycles A, B, and C. This compression type refrigerator 10-3 is the structure which added the refrigerating cycle C to the compression type refrigerator 10-2 shown in FIG. The extraction device 33 is connected to the condenser 13-3 of the refrigeration cycle C. The refrigeration cycle C includes an evaporator 11-3, a compressor 12-3, a condenser 13-3, and an expansion valve 14-3. The refrigerant vapor evaporated in the evaporator 11-3 is compressed by the compressor 12-3. The compressed refrigerant vapor is cooled and condensed by the condenser 13-3 to be liquefied, and the liquefied refrigerant is returned to the evaporator 11-3 through the expansion valve 14-3 to constitute a refrigeration cycle. .

  An extraction pipe L for extracting refrigerant gas from the condenser 13-2 of the refrigeration cycle B is connected to the evaporator 11-3 of the refrigeration cycle C via the orifice 31. The non-condensable impurities in the condenser 13-2 of the refrigeration cycle B move to the evaporator 11-3 of the refrigeration cycle C together with the extracted refrigerant gas (refrigerant vapor). In the refrigeration cycle C, non-condensable impurities circulate together with the refrigerant, and finally accumulate in the condenser 13-3 of the refrigeration cycle C. The accumulated non-condensable impurities are discharged out of the system by the extraction device 33 provided in the refrigeration cycle C.

  On the other hand, the refrigerant quantity gradually increases in the refrigeration cycle C due to the moving refrigerant. The amount of increase in the refrigerant can be detected by monitoring the refrigerant liquid level in the evaporator 11-3 and the refrigerant liquid level in the condenser 13-3. Here, by providing the overflow weir 23 on the side surface of the evaporator 11-3, when the refrigerant liquid level in the evaporator 11-3 rises, the refrigerant liquid overflowing beyond the overflow weir 23 passes through the valve 25. It is sent to the evaporator 11-2 and returned to the refrigeration cycle B. Further, the refrigerant amount gradually increases in the refrigeration cycle B due to the refrigerant moving from the refrigeration cycle C to the refrigeration cycle B. The amount of increase in the refrigerant can be detected by monitoring the refrigerant liquid level in the evaporator 11-2 and the refrigerant liquid level in the condenser 13-2. Here, by providing the overflow weir 22 on the side surface of the evaporator 11-2, when the refrigerant liquid level in the evaporator 11-2 rises, the refrigerant liquid that overflows beyond the overflow weir 22 passes through the valve 24. It is sent to the evaporator 11-1 and returned to the refrigeration cycle A.

  The evaporator 11-1 of the refrigeration cycle A is provided with an impurity concentrating device 32, the refrigerant liquid level of the evaporator 11-1 is increased, and the overflow weir 21 provided on the side surface of the evaporator 11-1. When the value exceeds, the overflowing refrigerant liquid moves to the concentrating device 32, whereby the impurities are recovered. In this way, by providing one impurity removal device comprising one extraction device 33 and one concentration device 32, impurities are simultaneously recovered from three independent refrigeration cycles A, B, and C. be able to. In this example, three independent refrigeration cycles A, B, and C are shown as an example. However, even in the case of more independent refrigeration cycles, each refrigeration cycle can be achieved by one bleeder and one concentrator. Impurities can be recovered simultaneously from the cycle.

  FIG. 6 is a diagram showing a schematic configuration example of the compression refrigerator according to the present invention. The compression refrigerator 10-4 is a compression refrigerator having three independent refrigeration cycles A, B, and C, similar to the compression refrigerator 10-3 shown in FIG. This compression refrigerator 10-4 differs from the compression refrigerator 10-3 in that the extraction pipe L for extracting refrigerant gas from the condenser 13-1 in the refrigeration cycle A is connected to the evaporator 11- in the refrigeration cycle C. 3 through an orifice 31. The bleeder 33 for removing non-condensable impurities accumulated in the condenser 13-3 of the refrigeration cycle C is removed, and the condenser 13-1 of the refrigeration cycle A and the evaporator 11-2 of the refrigeration cycle B are further replaced. The extraction piping L to be connected, the extraction piping L connecting the condenser 13-2 of the refrigeration cycle B and the evaporator 11-3 of the refrigeration cycle C are removed. And the point which has provided the concentration apparatus 32 for collect | recovering impurities in the evaporator 11-1 of the refrigerating cycle A is the same as the compression refrigerator 10-3.

  Unlike the compression refrigerator 10-4, an extraction device for removing non-condensable impurities is not provided, and a concentrating device 32 for recovering liquid impurities is provided only in the evaporator 11-1 of the refrigeration cycle A. Even if it is provided, it is necessary to move the refrigerant amount corresponding to the refrigerant moved as the refrigerant liquid in the direction opposite to the movement of the refrigerant liquid. In this case, it is not particularly necessary to move the refrigerant vapor from the condenser where non-condensable impurities are likely to accumulate.If the direction is to compensate for the decrease in the refrigerant amount in each refrigeration cycle, the refrigerant is extracted from where and where You may move to. Here, as the simplest method, the condenser 13-1 of the refrigeration cycle A and the evaporator 11-3 of the refrigeration cycle C are connected by the extraction pipe L through the orifice 31, and the refrigerant vapor is supplied from the condenser 13-1. The evaporator 11-3 is steadily moved, and similarly to the compression refrigerator 10-3 shown in FIG. 5, the evaporators 11-1, 11-2, 11- of the refrigeration cycles A, B, C are used. 3 are provided with overflow weirs 21, 22, 23, respectively, and the refrigerant liquid of the evaporators 11-1, 11-2, 11-3 exceeding the overflow weirs 21, 22, 23 passes through the motor-operated valves 24, 25. It is made to move to 11-1, 11-2, 11-3.

  By setting the compression refrigerator 10-4 to the above configuration, the amount of refrigerant in the evaporator 11-3 of the refrigeration cycle C increases as a result. The refrigerant exceeding the overflow weir 23 of the evaporator 11-3 increases the amount of refrigerant in the evaporator 11-2 of the refrigeration cycle B, and further exceeds the overflow weir 22 of the evaporator 11-2 of the refrigeration cycle B. Thus, impurities in the refrigerant are sequentially accumulated in the evaporator 11-1 of the refrigeration cycle A so that the refrigerant in the evaporator 11-1 of the refrigeration cycle A increases. The evaporator 11-1 of the refrigeration cycle A is provided with a concentrating device 32 for collecting impurities, and the refrigerant liquid level of the evaporator 11-1 is increased and provided on the side surface of the evaporator 11-1. When the overflow weir 21 is exceeded, the overflowing refrigerant liquid moves to the concentrating device 32, whereby the impurities are recovered.

  In the above embodiment, the compression type refrigerator and the double cycle compression type refrigerator having a plurality of independent refrigeration cycles have been described. However, the compression refrigerator according to the present invention has one refrigeration cycle. It may be a compression type refrigerator composed of a plurality of refrigerators.

  The embodiments of the present invention have been described above. However, the present invention is not limited to the above-described embodiments, and various modifications can be made within the scope of the technical idea described in the claims and the specification and drawings. Can be modified. For example, in the above embodiment, the compression apparatus includes both the extraction device for removing noncondensable gas and the concentration device (liquid impurity recovery means) for removing liquid impurities such as lubricating oil, or only the concentration device. Although the type refrigerator is shown, it may be a compression refrigerator having only an extraction device.

  The present invention relates to an extraction gas moving means for extracting a refrigerant gas containing gaseous impurities from one refrigeration cycle and moving it to another refrigeration cycle, and a refrigerant liquid containing liquid impurities from another refrigeration cycle. The gaseous liquid is extracted into the refrigerant liquid moving means for moving the gas to the other refrigeration cycle in the direction opposite to the moving direction of the gas moved by the extraction gas moving means, and the final stage refrigeration cycle for moving the gas by the extraction gas moving means. An extraction device for discharging outside the system and a concentrating device for extracting liquid impurities and discharging them outside the system are provided in the final stage refrigeration cycle in which the refrigerant liquid is moved by the refrigerant liquid moving means. By providing a stand concentration device, it can be used to provide a compression refrigerator that can remove impurities from a plurality of refrigeration cycles at low cost.

10-1 to 3 Compression refrigerator 11-1 to 3 Evaporator 12-1 to 3 Compressor 13-1 to 3 Condenser 14-1 to 3 Expansion valve 21 to 23 Overflow weir 24 Motor operated valve 31 Orifice 32 Concentrator 33 Extraction device 41 Low pressure side evaporator 42 Low pressure side compressor 43 Low pressure side condenser 44 Low pressure side expansion valve 46 Overflow weir 51 High pressure side evaporator 52 High pressure side compressor 53 High pressure side condenser 54 High pressure side expansion valve 61 Orifice 62 Concentration Device 63 Bleed device 64 Automatic valve

Claims (6)

An evaporator, a compressor, a condenser, and an expansion valve are provided, heat is taken from the fluid to be cooled by the evaporator to evaporate the refrigerant, the evaporated refrigerant vapor is compressed by the compressor, and the compressed refrigerant vapor A plurality of refrigerators having a refrigeration cycle configured to cool the refrigerant with a cooling fluid in the condenser and expand the condensed refrigerant liquid through the expansion valve and return the refrigerant liquid to the evaporator, or a plurality of the refrigeration cycles. In the compression refrigerator provided,
Extraction gas moving means for extracting a refrigerant gas containing gaseous impurities from one refrigeration cycle and moving the refrigerant gas to another refrigeration cycle;
A bleeder that bleeds the gaseous impurities to the refrigeration cycle of the final stage in which gas is moved by the bleed gas moving means, and discharges it out of the system ;
A refrigerant liquid moving means for moving a refrigerant liquid containing liquid impurities from another refrigeration cycle to the other refrigeration cycle in a direction opposite to the moving direction of the gas moving by the extraction gas moving means;
A compression type refrigerator having a liquid impurity recovery means for extracting the liquid impurities and discharging them out of the system in a final refrigeration cycle in which the refrigerant liquid is moved by the refrigerant liquid moving means . In the compression refrigerator according to claim 1 ,
The extraction gas moving means includes an extraction pipe for moving a refrigerant gas containing gas impurities extracted from the one refrigeration cycle, and provided with a flow rate limiting means for limiting the flow rate of the gas flowing through the extraction pipe. A featured compression refrigerator. The compression refrigerator according to claim 1 or 2 ,
The refrigerant liquid moving means moves the refrigerant liquid containing the liquid impurities from the evaporator of the downstream refrigeration cycle of the gas moved by the extraction gas moving means to the evaporator of the one-stage upstream refrigeration cycle. And a control means for controlling the refrigerant liquid that moves through the refrigerant moving pipe. The compression type refrigerator according to any one of claims 1 to 3 ,
The compression type refrigerator is characterized in that the liquid impurity collecting means is a concentrating device for extracting the liquid impurities by superheating and concentrating the refrigerant liquid. The compression type refrigerator according to any one of claims 1 to 4 ,
The plurality of refrigeration cycles are a low pressure side refrigeration cycle and a high pressure side refrigeration cycle,
The extraction gas moving means moves the refrigerant gas containing gaseous impurities from the condenser of the low-pressure side refrigeration cycle to the condenser of the high-pressure side refrigeration cycle. The compression refrigerator according to claim 5 ,
The refrigerant liquid moving means moves the refrigerant liquid containing liquid impurities from the evaporator of the high-pressure side refrigeration cycle to the evaporator of the low-pressure side refrigeration cycle.

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