US3864934A - Cooling pump system - Google Patents

Cooling pump system Download PDF

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Publication number
US3864934A
US3864934A US291026A US29102672A US3864934A US 3864934 A US3864934 A US 3864934A US 291026 A US291026 A US 291026A US 29102672 A US29102672 A US 29102672A US 3864934 A US3864934 A US 3864934A
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United States
Prior art keywords
closed container
compressor
liquid
cooling medium
medium
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Expired - Lifetime
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US291026A
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English (en)
Inventor
Carl-Eric Christian Jeding
Vagn Hovgaard Villadsen
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Johnson Controls Denmark ApS
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Thomas Ths Sabroe and Co
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor

Definitions

  • ABSTRACT An apparatus having a heat developing part such as a compressor in a refrigeration system, said part being adapted to be cooled by a cooling medium supplied thereto by means of a pump.
  • control means being provided for regulating the supply of cooling medium in response to actual cooling requirements of the heat developing part characterized in that the pump is at least partly constituted by a thermal positive displacement pump of the type comprising a closed container partly filled with a liquid pumping medium.
  • said container having a lower outlet pipe for said pumping liquid and an inlet pipe connected to a pumping liquid I reservoir through inlet control'means operable to effect refilling of pumping liquid into the container the container being in heat conducting connection wit-h a heating source operable to heat the container so as to increase the vapour pressure in the container suffi- 1 ciently to cause liquid to be pressed out through said outlet pipe for thereby causing said cooling medium to be supplied to said heat developing part, the pumping liquid and the cooling medium preferably being identical whereas the container is placed in heat conducting connection with the heat developing part which thus at least partly constitutes the said heating source.
  • PATENTEDFEBI 1 I 1 PATENTEUFEBI 1 1915 SHEET 2 0? a FIG la 3,864,934 SHEET 30F 3 PATENTEDFEBI wars COOLING PUMP SYSTEM
  • the present invention relates to an apparatus having a heat developing part such as a compressor in a refrigeration system, said part being adapted to be cooled by a cooling medium supplied thereto by means of a pump, control means being provided for regulating the supply of cooling medium in response to actual cooling requirements of the heat developing part.
  • the object of the present invention is to provide an apparatus of the type mentioned in which the supply of cooling medium can be effected in an extremely simple manner and with negligible extra power consumption.
  • thepump is at least partly constituted by a thermal positive displacement pump of the type comprising a closed container partly filled with a liquid pumping medium, said container having a lower outlet pipe for said pumping liquid and an inlet pipe connected to a pumping liquid reservoir through inlet control means preferably for intermittent admission of pumping liquid into the container, the container being in heat conducting connection with a heating source operable to heat the container so as to increase the vapour pressure in the container sufficiently to cause liquid to be pressed out through said outlet pipe for thereby causing said cooling medium to be supplied to said heat developing part, the pumping liquid and the cooling medium preferably being identical, whereas the container is placed in heat conducting connection with the heat developing part which thus at least partly constitutes the said heating source.
  • cooling pump may automatically adjust its output to suit the directly ascertained cooling requirement, namely as expressed by the actual heat influence on the pump container so that the supply of cooling medium will be regulated as desired without any kind of special sensing and regulating devices.
  • the arrangement according to the invention will be extremely simple and advantageous, because a part of the liquid coolant in the system may be used directly as the cooling medium for the compressor, i.e., the'cooling medium may be taken from the coolant system without the use of any special reservoir, and after its use it may simply be reintroduced into the coolant system.
  • the liquid coolant is well suited to constitute the medium handled by the thermal pump.
  • FIG. 1 is a schematic diagram of a refrigerating plant made according to the invention
  • FIG. la is a schematic diagram of another embodiment of the refrigerating plant of FIG. I.
  • FIG. 2 is a perspective view of the compressor of the:
  • FIG. 3 is a plan end view, partly in cross-section, of-
  • FIG. 4 is a schematic diagram of a modified embodiment of the systems according to the invention.
  • FIG. 5 is a corresponding view of still a further embodiment.
  • the numeral 2 designates a refrigerating compressor which through a pressure pipe 4 sends a compressed gaseous coolant to a condenser 6 thereby sending the gas through'an oil seperator 8.
  • the cooling medium is conducted through a pipe 10 past a thermostatic expansion valve 12 to an evaporator 14 from which a pipe 16 leads back to the suction side of the compressor 2.
  • a temperature sensor 18 which controls the valve 12; the system so far described is a conventional refrigeration system.
  • a container 20 On the oil separator 8 (or directly on the compressor 2 as mentioned below) is placed a container 20 which through a non-return valve 22 in a pipe 24 is connected to the pipe 10 between the condenser 6 and the expansion valve 12, and which at the top is connected to the suction pipe 16 by means of a pipe 26 in which is placed a solenoid valve 28 and a pressure control valve 30.
  • the container 20 At the bottom the container 20 is connected via a pipe 32 to a heat exchanger 34 in direct connection with the compressor 2, the outlet from this heat exchanger being connected to the discharge side of the compressor through a pipe 36.
  • a throttle valve 38 In the pipe 32 there is interposed a throttle valve 38 and a non-return valve 40.
  • the float 42 When the container 20 is empty the float 42 will open the valve 28 whereby the container is connected to the suction side of the compressor through the pipe 26. The result will be that cooling liquid will be sent from the pipe through the non-return valve 22 into the container until the float at an upper liquid level causes the valve 28 to close. After this point there will be a further, slight inflow until the space above the liquid is narrowed down so much that the correspondingly increasing pressure in it will counterbalance the charging pressure in the pipe 10.
  • the flow of cooling medium to this section will thus be determined by the pressure or pressure development in the container 20, and as the container is placed in heat conducting connection with the oil separator, which in its turn receives heat from the compressor by way of the hot gaseous cooling medium, the vapour pressure in the container will fluctuate with the compressor temperature so that this pressure tends to increase with the temperature of the compressor and thereby cause a graduated flow of liquid to be pressed through the cooling section 34.
  • the temperature nor the pressure inside the container will vary very much since the medium will merely boil more or less so as to be pressed out according to the rate of boiling. It will be seen that the cooling in this way will regulate itself according to requirement and that no external power is used for the forward pumping of the cooling medium.
  • the pressure pipe 10 is connected to the suction pipe 16 of the compressor through the pipes 24 and 26, but the pressure regulating valve 30 is set at a pressure which is only slightly lower than the condensing pressure so that the pressure drop in the pressure pipe will not be more than strictly necessary i.e., in practice of no specialsignificance.
  • the cooling section 34 in the compressor may as already mentioned be a regular heat exchanger, but the cooling may also be effected by direct injection of the cooling medium into a cooling compartment connected to the discharge side of the high side of the compressor.
  • the pump container 20 may be installed in connection with any part of the compressor system or the refrigerating plant whose temperature during operation is higher than the condensing temperature and besides fluctuates with the development of heat in the compressor.
  • FIGS. 2 and 3 show a preferred location on a piston type compressor 50 with cylinders 54 protruding from a crankcase 52 in well known manner. In the wall of the crankcase is in the usual way provided an admission opening, which is closed with a cover 56. Corresponding covers 58 may be placed over openings in the compressor house in order to give admission to the top of the cylinders.
  • the container may, according to the present incover itself may even constitute the front sidev of the box.
  • This mounting arrangement is simple to perform and will offer no obstruction to the servicing of the crankcase as the box 60 is easily removed for that purpose by unscrewing the cover 56.
  • non-return valve 22 in the pipe 24 it is possible, if desired, to employ a solenoid valve 22' controlled by the float switch 44 through a wire 45a as shown in FIG. 1a.
  • solenoid valve 28 may be employed a needle valve or similar type of valve located in connection with the container 20 and in a manner not shown controlled directly by the float 42.
  • the said float it may also be possible instead of the said float to employ any suitable type of level detector arrangement for controlling the valve 28 or the valve 22.
  • the cooling medium of the plant As here described it is possible in the case of a refrigerating plant to employ the cooling medium of the plant as a cooling medium for the heat developing part, but it is perfectly possible to circulate the cooling medium in a separate system with a reservoir to which the medium is conducted from the refrigerating section, and from which it is conducted to the container 20 controlled e.g., by the float valve.
  • FIG. 5 A system of this type is shown in FIG. 5 where parts similar to the different parts of FIG. 1 are designated with the same reference mumerals.
  • a special reservoir 23 from which the combined pumping and cooling medium is conducted to the pump container through the pipe 24 and through the valve 22 which is here a solenoid valve controlled by the level detector switch 44.
  • the return pipe 36 from the cooling element 34 is connected to the top of the reservoir 23.
  • the pipe 26 serving to permit exhaust of the vapour or steam from the pump container 20 during refilling thereof is likewise connected to the top of the reservoir 23, as in FIG. I through a solenoid valve 28.
  • the pump 20 will be able to continue to be active some time after the compressor is stopped, and especially in the case of direct injection of the cooling medium into the compressor as described in connection with FIG. 1 this may result in an unwanted accumulation of cooling medium in it; in order to counter this effect there should be provided means to stop the pumping when the compressor stops, e.g., a solenoid valve 21 located in the supply pipe 24 to the pump container 20, and operatively connected with the power supply to the compressor so as to be open when the compressor is working and close as soon as the compressor is stopped, as illustrated, for example, in FIG. I.
  • a solenoid valve 21 located in the supply pipe 24 to the pump container 20
  • An essential feature of the present invention is that the use of the thermal pump gives automatic control of the pump output when the pump is heated from the part which is to be cooled, and for that matter it would be of minor'importance if it was necessary to use a small external source of energy, for instance to produce a direct pumping of cooling medium into the container 20 against an unrelieved pressure in it so that the filling operation does not necessarily have to be intermittent; in this case the feeding pump should be controlled by the level detector so as to be operative when the liquid level in the container 20 is below a predetermined maximum level. It is true that it would then instead be possible to use a pump which simply pumps the liquid up to the cooling section, but by omitting the container 20 the automatic regulation would get lost.
  • the driving agent in thermal pumping does not necessarily have to be identical with the medium to be pumped, and it will be understood that the present invention is not limited to the situation where driving medium, pumping medium and possibly also the coolant in a refrigeration system are identical.
  • the output liquid from the container may be used for driving a hydraulic motor 62 of the positive displacement type instead of as shown in FIG. 4 being supplied to the cooling section 34; otherwise the pump circuit in connection with the pump container 20 is identical with that shown in FIG. 4, and the same reference numerals are used.
  • the hydraulic motor 62 drives a rotary pump 64 of the positive displacement type, this pump serving 'to supply cooling liquid through a pipe 66 from a reservoir 68 to the cooling section 34 from which the return pipe 36 leads back to the reservoir, if necessary through an external heat exchanger 70 in which the cooling medium may be cooled or condenced.
  • the cooling medium is not heated in the pump container whereby it may have a very high cooling capacity and the proportion between the rate of flow of the two media need not be one to one. i.e., the cooling medium may be supplied in a proportional manner with twice or more the flow rate of the pumping medium.
  • the liquid to be heated in the pump container for pumping purposes may be liquid coolant such as Freon having a boiling point substantially below 100C, since the automatic control of the pumping may thereby be accomplished in an effective and easy manner at relatively low temperatures. It will be understood that this advantage is entirely independent'of the possible additional use of the coolant for cooling purposes. However, it is of course a further advantage that a medium having optimal properties for acting as the pumping medium may thus additionally as described in connection with FIG. 1 and 4 be used for the actual cooling, likewise with optimal properties for this purpose.
  • the cooling medium is of the type such as Freon which provided cooling by evaporation in the cooling section the actual cooling temperature will be much lower than the temperature of the liquid in the pump container 20 (FIGS. 1 and 4).
  • the pump container should not be placed adjacent the hottest zone of the heat developing part, since the cooling medium could then itself be heated too much to be effective for cooling purposes, especially of course if the medium has a relatively high boiling point; preferably there should not be built up any excessive overpressure in the pump container, so the temperature of the liquid therein will not normally be able to exceed the normal boiling point of the liquid.
  • the invention is not restricted to cooling of compressors, since other heat developing parts such as motor cylinders may be cooled in this manner.
  • An apparatus havinga heat developing part comprising:
  • control means for regulating the supply of said cool-g ing medium in response to heat generated by said heat developing part
  • said pump means including a thermal positive displacement pump of the type having a closed container partly filled with a liquid pumping medium,
  • said closed container including an outlet pipe for said liquid pumping medium, an inlet pipe for refilling said liquid pumping medium into said closed container, said inlet pipe being connected to a reservoir of said liquid pumping medium, and inlet control means for regulating said refilling of said closed container;
  • a heating source in heat conduction connectionwith said closed container for heating said closed container sufficiently to cause said liquid pumping medium in said closed container to boil so that the vapour pressure in said closed container is sufficiently increased to. cause the liquid pumping medium to be forced out through said outlet pipe for supplying said cooling medium to said heat developing part
  • said heat developing part at least partlyconstitutes said heating source in heat conduction connection with said closed container so as to effectively cause the supply of the cooling liquid to be adjusted in direct response to the temperature variations of the heat developing part.
  • liquid pumping medium is a liquid coolant of the type having a boiling point substantially below C.
  • said heat developing part is a compressor in a refrigerating system of the type working with a cooling medium which in a gaseous phase is compressed in the compressor, thereafter condensed into a liquid phase at the pressure side of the compressor then evaporated after passage of an expansion valve and finally returned to the suction side of the compressor, and in which the pumping and cooling medium is constituted by the cooling medium circulating in the refrigerating system, characterized in that said closed container is in heat conducting connection with the compressor having a temperature which is equal to or bigger than the condensing temperature of the refrigeration system and fluctuates with the working conditions of the compressor, whereas the inlet pipe of said closed container is connected to that part of the refrigeration system in which the cooling medium is present as a liquid under pressure, while the top of said closed container is connected to a point of relatively lower pressure of said refrigeration system through intermittently operating valve means.
  • An apparatus further comprising an oil separator unit mounted in the-discharge pipe from the compressor, wherein said closed container is mounted in direct heat exchanging connection with said oil separator unit.
  • said inlet control means are operable to effect intermittent refilling of said closed container, and in which the upper space of said closed container is connected to venting means operable to relieve the pressure inside said closed container during said refilling.
  • detector means for detecting the level of the liquid in said closed container are operatively connected with said inlet control means so as to cause refilling in response to said liquid pumping medium falling below a predetermined level.
  • said inlet control means comprise valve means operable to actuate the said venting means, said liquid pumping medium being supplied to said closed container through a one-way valve under a pressure which is higher than the relieved pressure in said closed container but lower than the vapour pressure of said liquid pumping medium.
  • inlet control means comprise valve means operable to actuate said venting means and inlet valve means operableconcurrently therewith to introduce liquid into said closed container.
  • An apparatus comprising:
  • said compressor being a piston type compressor having a crankcase and cylinders protruding from said crankcase, said piston type compressor having a detachable cover mounted over an admission opening of said crankcase;
  • control means for regulating the supply of said cooling medium in response to heat generated by said compressor
  • said pump means including a thermal positive displacement pump of the type having a closed container partly filled with a liquid pumping medium and mounted protruding inwardly into said crankcase at the back of said cover, said liquid pumping medium constituting said cooling medium circulating in said refrigeration system and having a boiling point substantially below C,
  • said closed container including a lower outlet pipe for said liquid pumping medium, an inlet pipe for refilling said liquid pumping medium into said closed container, said inlet pipe being connected to a reservoir of said liquid pumping medium at a portion of said refrigeration system in which said liquid pumping medium is under pressure, an inlet control means for regulating said refilling of said closed container, said closed container being connected to the suction side of said compressor through intermittently operating valve means; and
  • a heating source including at least partly said compressor in heat conduction connection with said closed container for heating said closed container at a temperature equal to or larger than the condensing temperature of said refrigeration system, said temperature fluctuating with the working conditions of said compressor, sufficiently to cause said liquid pumping medium in said closed container to boil so that the vapour pressure in said closed container is sufficiently increased to cause the liquid pumping medium to be forced out through said lower outlet pipe for supplying said cooling medium to said compressor,
  • heating source including at least partly said compressor in heat conduction connection with said closed container effectively causes the supply of the cooling liquid to be adjusted in direct response to the fluctuations of temperature of the compressor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressor (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Air Conditioning Control Device (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Other Air-Conditioning Systems (AREA)
US291026A 1971-09-24 1972-09-21 Cooling pump system Expired - Lifetime US3864934A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DK465671AA DK136741B (da) 1971-09-24 1971-09-24 Anlæg med en varmeudviklende del, fortrinsvis en kølekompressor, som holdes kølet med et kølemedium.

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US3864934A true US3864934A (en) 1975-02-11

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US291026A Expired - Lifetime US3864934A (en) 1971-09-24 1972-09-21 Cooling pump system

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US (1) US3864934A (enrdf_load_stackoverflow)
JP (1) JPS555016B2 (enrdf_load_stackoverflow)
AU (1) AU471056B2 (enrdf_load_stackoverflow)
BR (1) BR7206565D0 (enrdf_load_stackoverflow)
CS (1) CS164935B2 (enrdf_load_stackoverflow)
DD (1) DD100072A5 (enrdf_load_stackoverflow)
DE (1) DE2245035A1 (enrdf_load_stackoverflow)
DK (1) DK136741B (enrdf_load_stackoverflow)
ES (1) ES407113A1 (enrdf_load_stackoverflow)
FR (1) FR2153285B1 (enrdf_load_stackoverflow)
GB (1) GB1375429A (enrdf_load_stackoverflow)
IT (1) IT967816B (enrdf_load_stackoverflow)
NL (1) NL7212966A (enrdf_load_stackoverflow)
NO (1) NO130655C (enrdf_load_stackoverflow)
PL (1) PL78442B1 (enrdf_load_stackoverflow)
SE (1) SE392335B (enrdf_load_stackoverflow)
SU (1) SU488430A3 (enrdf_load_stackoverflow)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5822999A (en) * 1996-05-03 1998-10-20 Electrolux Espana, S.A. Refrigeration system
US5946925A (en) * 1998-04-15 1999-09-07 Williams; Donald C. Self-contained refrigeration system and a method of high temperature operation thereof
US20050120733A1 (en) * 2003-12-09 2005-06-09 Healy John J. Vapor injection system
US20070039336A1 (en) * 2005-08-22 2007-02-22 Wu Man W Compressor with vapor injection system
US20070039347A1 (en) * 2005-08-22 2007-02-22 Gnanakumar Robertson Abel Compressor with vapor injection system
US20110185754A1 (en) * 2008-10-29 2011-08-04 Mitsubishi Electric Air-conditioning apparatus
CN105804972A (zh) * 2015-01-15 2016-07-27 周文三 可对马达散热的打气机设备组结构
CN104956163B (zh) * 2013-01-25 2017-05-17 特灵国际有限公司 具有制冷剂蒸汽通风管线的制冷剂降温和润滑系统

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS518210U (enrdf_load_stackoverflow) * 1974-07-02 1976-01-21
FR2474149A1 (fr) * 1980-01-22 1981-07-24 Sdecc Dispositif de recuperation des calories dissipees par un compresseur d'une pompe a chaleur
FR2487960A1 (fr) * 1980-07-29 1982-02-05 Unite Hermetique Dispositif d'amorcage pour circuit de refroidissement du compresseur d'une machine thermique a compression, et machine thermique a compression comportant un tel dispositif
JP5965732B2 (ja) * 2012-06-07 2016-08-10 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド 冷凍サイクル装置

Citations (4)

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Publication number Priority date Publication date Assignee Title
US2073123A (en) * 1935-01-31 1937-03-09 Gen Motors Corp Refrigerating apparatus
US2958209A (en) * 1958-11-03 1960-11-01 Basil G Egon Heat pump
US3192735A (en) * 1961-09-12 1965-07-06 American Radiator & Standard Cooling coil for hermetic motor using system refrigerant
US3416327A (en) * 1967-02-02 1968-12-17 Carrier Corp Refrigeration machine

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2073123A (en) * 1935-01-31 1937-03-09 Gen Motors Corp Refrigerating apparatus
US2958209A (en) * 1958-11-03 1960-11-01 Basil G Egon Heat pump
US3192735A (en) * 1961-09-12 1965-07-06 American Radiator & Standard Cooling coil for hermetic motor using system refrigerant
US3416327A (en) * 1967-02-02 1968-12-17 Carrier Corp Refrigeration machine

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5822999A (en) * 1996-05-03 1998-10-20 Electrolux Espana, S.A. Refrigeration system
US5946925A (en) * 1998-04-15 1999-09-07 Williams; Donald C. Self-contained refrigeration system and a method of high temperature operation thereof
US7299649B2 (en) 2003-12-09 2007-11-27 Emerson Climate Technologies, Inc. Vapor injection system
US20050120733A1 (en) * 2003-12-09 2005-06-09 Healy John J. Vapor injection system
US8037710B2 (en) 2005-08-22 2011-10-18 Emerson Climate Technologies, Inc. Compressor with vapor injection system
US7275385B2 (en) 2005-08-22 2007-10-02 Emerson Climate Technologies, Inc. Compressor with vapor injection system
US20070039347A1 (en) * 2005-08-22 2007-02-22 Gnanakumar Robertson Abel Compressor with vapor injection system
US20070039336A1 (en) * 2005-08-22 2007-02-22 Wu Man W Compressor with vapor injection system
US8695369B2 (en) 2005-08-22 2014-04-15 Emerson Climate Technologies, Inc. Compressor with vapor injection system
US20110185754A1 (en) * 2008-10-29 2011-08-04 Mitsubishi Electric Air-conditioning apparatus
EP2341295A4 (en) * 2008-10-29 2014-11-26 Mitsubishi Electric Corp AIR CONDITIONING
US9958175B2 (en) 2008-10-29 2018-05-01 Mitsubishi Electric Corporation Air-conditioning apparatus
CN104956163B (zh) * 2013-01-25 2017-05-17 特灵国际有限公司 具有制冷剂蒸汽通风管线的制冷剂降温和润滑系统
US9671146B2 (en) 2013-01-25 2017-06-06 Trane International Inc. Refrigerant cooling and lubrication system with refrigerant vapor vent line
US10458686B2 (en) 2013-01-25 2019-10-29 Trane International Inc. Refrigerant cooling and lubrication system with refrigerant vapor vent line
CN105804972A (zh) * 2015-01-15 2016-07-27 周文三 可对马达散热的打气机设备组结构

Also Published As

Publication number Publication date
DK136741B (da) 1977-11-14
NO130655C (enrdf_load_stackoverflow) 1975-01-15
SU488430A3 (ru) 1975-10-15
DK136741C (enrdf_load_stackoverflow) 1978-05-01
AU471056B2 (en) 1976-04-08
JPS4840012A (enrdf_load_stackoverflow) 1973-06-12
JPS555016B2 (enrdf_load_stackoverflow) 1980-02-02
CS164935B2 (enrdf_load_stackoverflow) 1975-11-28
AU4705672A (en) 1974-04-04
NO130655B (enrdf_load_stackoverflow) 1974-10-07
FR2153285B1 (enrdf_load_stackoverflow) 1976-10-29
DE2245035A1 (de) 1973-03-29
NL7212966A (enrdf_load_stackoverflow) 1973-03-27
DD100072A5 (enrdf_load_stackoverflow) 1973-09-05
PL78442B1 (enrdf_load_stackoverflow) 1975-06-30
ES407113A1 (es) 1975-11-01
BR7206565D0 (pt) 1973-07-19
FR2153285A1 (enrdf_load_stackoverflow) 1973-05-04
IT967816B (it) 1974-03-11
GB1375429A (enrdf_load_stackoverflow) 1974-11-27
SE392335B (sv) 1977-03-21

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