EP0667499B1 - Pneumatic ice making device - Google Patents

Pneumatic ice making device Download PDF

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Publication number
EP0667499B1
EP0667499B1 EP93906784A EP93906784A EP0667499B1 EP 0667499 B1 EP0667499 B1 EP 0667499B1 EP 93906784 A EP93906784 A EP 93906784A EP 93906784 A EP93906784 A EP 93906784A EP 0667499 B1 EP0667499 B1 EP 0667499B1
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EP
European Patent Office
Prior art keywords
air
ice
course
heat exchanger
cold air
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP93906784A
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German (de)
English (en)
French (fr)
Other versions
EP0667499A1 (en
EP0667499A4 (en
Inventor
Motohisa Uda
Isao Nikai
Junji Matsuda
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kajima Corp
Original Assignee
Kajima Corp
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Filing date
Publication date
Application filed by Kajima Corp filed Critical Kajima Corp
Publication of EP0667499A1 publication Critical patent/EP0667499A1/en
Publication of EP0667499A4 publication Critical patent/EP0667499A4/en
Application granted granted Critical
Publication of EP0667499B1 publication Critical patent/EP0667499B1/en
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Classifications

    • A—HUMAN NECESSITIES
    • A63—SPORTS; GAMES; AMUSEMENTS
    • A63C—SKATES; SKIS; ROLLER SKATES; DESIGN OR LAYOUT OF COURTS, RINKS OR THE LIKE
    • A63C19/00—Design or layout of playing courts, rinks, bowling greens or areas for water-skiing; Covers therefor
    • A63C19/10—Ice-skating or roller-skating rinks; Slopes or trails for skiing, ski-jumping or tobogganing
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/004—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being air
    • 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
    • F25C—PRODUCING, WORKING OR HANDLING ICE
    • F25C3/00—Processes or apparatus specially adapted for producing ice or snow for winter sports or similar recreational purposes, e.g. for sporting installations; Producing artificial snow
    • F25C3/02—Processes or apparatus specially adapted for producing ice or snow for winter sports or similar recreational purposes, e.g. for sporting installations; Producing artificial snow for ice rinks

Definitions

  • the invention relates to an air refrigerant ice forming equipment in which air is utilized as a working medium. More particularly, it relates to an air refrigerant ice forming equipment suitable for use in facilities for playing ice sports including bobsleigh, ice skate, ice hockey and other ice sports.
  • an air refrigerant refrigerator in which air is used as a working medium exhibits a coefficient of performance of about 0.8, which value is about 1/3 to 1/2 of the coefficient of performance of a refrigerator in which Freon is used as a working medium.
  • An object of the invention is to effectively form ice in facilities for playing ice sports without using Freon or ammonia as a working medium and without using brine as a cooling medium.
  • an air refrigerant ice forming equipment having the features of claim 1.
  • Fig. 1 is a system drawing of an air refrigerant ice forming equipment according to the invention showing an arrangement of various instruments and a flow of air.
  • the ice forming equipment comprises a closed passage for air circulation incorporating an air compressor 1, a compressed air cooler 2 for cooling the air compressed by the compressor 1 with heat transfer media outside the refrigeration cycle, an air expander 3 for expanding the air which has passed through the cooler 2 to provide cold air and a heat exchanger 4 for ice formation using the cold air which has passed the air expander 3, in the indicated order along the flow of air.
  • the ice forming equipment further comprises a heat exchanger 5 for heat recovery wherein the air before entering the air expander 3 is heat exchanged with the air which has passed through the heat exchanger 4 for ice formation.
  • the air whose cold heat has been recovered in the heat exchanger 5, is then returned to the air compressor 1 via a return pipe 6.
  • the heat exchanger 5 for heat recovery is an air to air heat exchanger as shown in Fig. 2.
  • air passages 16 and the other air passages 17 are vertically alternately formed in a plurality of clearances formed by a plurality of plates 15.
  • Each air passage 16 or 17 is divided into a plurality of narrow passages 18 or 19 in order to enhance the effectiveness of the heat exchanger.
  • air passage 16 (or 17) air which has been compressed by the compressor 1 is caused to pass, while through the air passage 17 (or 16) air which has come from the heat exchanger 4 for ice formation is caused to pass.
  • the warm air from the compressor 1 is cooled by heat exchange with the cold air from the heat exchanger 4. Whereas the cold air coming from the heat exchanger 4 for ice formation is warmed and thus, the temperature of air returned to the air compressor 1 via the return pipe 6 is raised. As a result, the coefficient of performance of the refrigeration cycle is enhanced.
  • the compressed air cooler 2 for cooling the air coming from the compressor 1 comprises two heat exchangers 2A and 2B.
  • the heat exchanger 2A can be a shell and tube heat exchanger, as shown in Fig. 3, which comprises a shell 20 and a plurality of U tubes 21 incorporated in the shell 20.
  • the shell 20 is provided with a water inlet 22 and a water outlet 23 at one end thereof.
  • the water inlet 22 is communicated with the water outlet 23 by means of the U tubes 21.
  • the shell 20 is further provided with an air inlet 24 and an air outlet 25'.
  • cooling water is introduced from the water inlet 22, caused to pass through the U tubes and withdrawn from the water outlet 23.
  • tap water may be used as the cooling water.
  • the compressed air from the compressor 1 is introduced through the air inlet 24 into the inside of the shell 20 and withdrawn from the air outlet 25'.
  • the compressed air is cooled by heat exchange with the cooling water in the inside of the shell 20.
  • the heat exchanger 2B is an air to air heat exchanger, which may be of the same type as the heat exchanger 5 for heat recovery shown in Fig. 2. Cooling air usable in the heat exchanger 2B must be of a low temperature. In the winter season ambient atmospheric air can be used as such as the cooling air.
  • the air compressor 1 is for forcibly compressing air of atmospheric pressure by means of a rotating power of a power means 7 to provide compressed air, for example, having a pressure of 2 atmospheres.
  • the air compressor 1 can be a biaxial screw type compressor whose structure in itself is known in the art.
  • the biaxial screw type compressor as shown in Figs. 4 and 5, includes a male rotor 25 having screw vanes and a female rotor 27 having screw grooves which engage each other. By rotation of the rotors in the opposite directions air undergoes volume changes in the screw grooves and is compressed.
  • a shaft 26 of the male rotor 25 and a shaft 28 of the female rotor 27 are in gear by means of gears 29 and 30 so that they may rotate in the opposite directions.
  • the rotation of the power means 7 is transmitted to the shaft 26 and the rotors 25 and 27 are caused to rotate in the opposite directions. Air inhaled through a suction inlet 31 is gradually compressed by the rotation of the rotors 25 and 27 to a pressure of about 2 atmospheres and exhaled through an outlet 32.
  • the power means shown in Fig. 5 is a motor.
  • the air expander 3 is a biaxial screw type air expander having a structure symmetric to that of the air compressor 1, as shown in Figs. 5 and 6.
  • a shaft 36 of a male rotor 35 and a shaft 38 of a female rotor 37 are in gear by means of gears 39 and 40 so that they may rotate in the opposite directions.
  • the compressed air introduced into the air expander 3 through an inlet 41 causes the rotors 35 and 37 to rotate by its pressure and the air itself is adiabatically expanded to a pressure slightly higher than the atmospheric pressure and its temperature is decreased.
  • the cold air so formed is exhaled through an outlet 42.
  • the shaft 36 of the male rotor 35 of the air expander 3 is coupled to a driving shaft 43 of the power means 7 via a one-way clutch 44.
  • the one-way clutch 44 includes, as shown in Fig. 7, an outer ring 46 and an inner ring 47 and a plurality of cams 45 disposed in an annular space between the outer and inner rings 46 and 47.
  • the cams 45 are arranged obliquely against a radial direction common to the outer and inner rings 46 and 47. By this oblique arrangement of the cams 45, rotation can be transmitted one-way between the outer and inner rings.
  • the structure of the one-way clutch 44 itself is well known in the art.
  • the rotating energy of the rotors 35 and 37 of the air expander 3 can be transmitted to the driving shaft 43 of the motor 7 and recovered as a part of the driving power for the air compressor 1.
  • the driving power for the air compressor 1 may be obtained from a heat engine 50 for a cogeneration purpose, that is from a driving shaft 51 of an electric generator 50.
  • the driving shaft 51 of the heat engine 50 is coupled to the driving shaft 26 of the compressor 1 via a variable speed gear 52.
  • a hot exhaust gas obtained by combustion of fuel is sent to an exhaust gas boiler, from which high pressure steam is obtained.
  • the used exhaust gas is heat exchanged with cooling water and thereafter exhausted outside the system.
  • Warm water is obtained from the cooling water of the heat engine 50.
  • the power for driving the air compressor 1 is obtained from an exhaust gas turbine of the heat engine 50 for cogeneration purpose.
  • the surplus power of the heat engine 50 may be used as a power for electric generation or as a power for driving other power machines.
  • the rotating power of the heat engine 50 is fully utilized as a whole, primarily for operating the ice forming equipment according to the invention and the remaining for accumulation of electricity or other purposes in accordance with particular conditions for driving the ice forming equipment.
  • the heat exchanger 4 for ice formation is a heat exchanger for forming ice layers on outer surfaces thereof by passing therethrough cold air which has been formed by the air expander 3.
  • the heat exchanger 4 for ice formation is buried beneath the ice level, for example of an ice course for playing bobsleigh or luge or of an ice rink for playing ice skate or ice hockey for a purpose of forming necessary ice layers on the outer surfaces of the heat exchanger 4.
  • the heat exchanger 4 for ice formation may be composed of a plurality of pipes arranged in accordance with the desired particular position and shape of the ice layers.
  • Facilities for playing ice sports may be provided with the heat exchangers for ice formation in the form of an extended surface coil heat exchanger or in the form of a plane heat exchanger comprising a heat conducting material having a plurality of pipes buried therein.
  • Fig. 9 shows a course 53 for playing bobsleigh or luge.
  • the illustrated course 53 having a length of about 1.3 kilometers is divided into 7 parts 1 to 7, each part having an individually controlled ice forming equipment.
  • solid double circles indicate the positions where the ice forming equipment are disposed. Passages for air circulation of the adjacently disposed ice forming equipment are connected to each other by means of a by-path so as to back up a trouble which may be caused when one of the adjacent equipment gets out of order.
  • the course 53 begins at a starting point 53a and ends at a finish point 53c. Slightly downstream of the starting point 53a there is provided a starting point 53b for junior. Between the starting points 53a, 53b and the finish point 53c, there is provided a passage 54 for carrying back vehicles from the finish point 53c to the starting points 53a, 53b.
  • Fig. 10 is a piping layout of a heat exchanger 4 for ice formation buried in the course 53
  • Fig. 11 is a plan view of the piping of the heat exchanger 4 for ice formation.
  • On one side of the course there are provided a cold air supply pipe 55a and a cold air return pipe 56b, while on the other side of the course there are provided a cold air supply pipe 55b and a cold air return pipe 56a.
  • One end 57a of the cold air supply pipe 55a is communicated with the air expander, while the other end 58a of the cold air supply pipe 55a is closed.
  • one end 57b of the cold air supply pipe 55b is communicated with the air expander, while the other end 58b of the cold air supply pipe 55b is closed.
  • the cold air return pipes 56a, 56b are U-shaped pipes with one end 59a, 59b communicated with the heat exchanger for heat recovery and the other end 60a, 60b closed.
  • the cold air supply pipe 55a on one side of the course 53 makes a pair to the cold air return pipe 56a of the other side of the course 53.
  • the cold air supply pipe 55b on the other side of the course 53 makes a pair to the cold air return pipe 56b of one side of the course 53.
  • the cold air supply pipe 55a and return pipe 56a making a pair to each other are communicated by a plurality of ice forming pipes 61a disposed in parallel across the course beneath the level of ice.
  • the cold air supply pipe 55b and return pipe 56b making a pair to each other are communicated by a plurality of ice forming pipes 61b disposed in parallel. As shown in Fig. 10, the ice forming pipes 61a and 61b are arranged alternately.
  • the cold air prepared in the air expander 3 is divided into two which are respectively introduced into the cold air supply pipes 55a, 55b through their open ends 57a, 57b. Since the other ends 58a, 58b of the supply pipes 55a, 55b are closed, the cold air supplied is caused to pass through the ice forming pipes 61a, 61b, recovered in the cold air return pipes 56a, 56b, combined together and sent into the return passage 6.
  • Fig. 12 is a cross-sectional view of a linear portion of a course for playing bobsleigh provided with an ice forming equipment according to the invention.
  • the reference numeral 65 designates a concrete base; 66 a concrete plate; and 67 a heat insulating mortar layer.
  • On both sides of the course side covers 68a and 68b are respectively provided. Inside the side cover 68a there are contained the cold air supply pipe 55a, the cold air return pipe 56b and a tap water pipe 69. Inside the side cover 68b there are contained the cold air supply pipe 55b, the cold air return pipe 56a and a warm water pipe 70.
  • a plurality of ice forming pipes 61a communicating the cold air supply pipe 55a and return pipe 56a and a plurality of ice forming pipes 61b communicating the cold air supply pipe 55b and return pipe 56b are alternately disposed in parallel across the course as shown in Fig. 11.
  • Upper surfaces of the ice forming pipes 61a and 61b are covered by a heat conducting mortar layer via a wire mesh.
  • the heat conducting mortar layer contains metallic powder dispersed therein.
  • the cold air prepared by the air expander 3 is sent into the cold air supply pipes 55a, 55b disposed inside the side covers 68a, 68b.
  • the cold air is then caused to pass through the ice forming pipes 61a, 61b buried in the course, recovered in the return pipes 56a, 56b, caused to pass through the heat exchanger 5 for heat recovery and the return passage 6 and returned to the air compressor 1.
  • the ice forming equipment according to the invention is designed so that a part of the cold air prepared by the air expander 3 may be discharged through an air discharge port 8 which may comprise a valve or damper 9 and a nozzle 10 (see Fig. 1).
  • an air discharge port 8 which may comprise a valve or damper 9 and a nozzle 10 (see Fig. 1).
  • a port 12 for sucking atmospheric air provided with a valve or damper 11 is connected to the return passage 6 on its way from the heat exchanger 5 for heat recovery to the air compressor 1, as shown in Fig. 1.
  • Suitable dry dehumidifiers include a Munter's dehumidifier (rotary dehumidifier having a function of reproducing the spent hygroscopic agent) and a two-tower dehumidifier wherein dehumidification of air and reproduction of the spent hygroscopic agent are alternately carried out (Fig. 1 illustrates a two-tower dehumidifier).
  • Fig. 13 is a cross-sectional view of a curved portion of a course for playing bobsleigh provided with an ice forming equipment according to the invention.
  • the basic construction of the curved course is substantially the same as that of the linear course shown in Fig. 12.
  • the reference numeral 75 designates a concrete base; 76 a concrete plate; and 77 an adiabatic mortar layer.
  • the heat insulating mortar layer 77 has an L-shaped cross-section so as to form a bank.
  • side covers 78a and 78b are provided on both sides of the course. Inside the side cover 78a there are contained the cold air supply pipe 55a, the cold air return pipe 56b and a tap water pipe 79.
  • a plurality of ice forming pipes 61a communicating the cold air supply pipe 55a and return pipe 56a and a plurality of ice forming pipes 61b communicating the cold air supply pipe 55b and return pipe 56b are alternately disposed in parallel across the course.
  • an air discharge port 8 is provided for discharging cold air from the cold air supply tube 55b.
  • a nozzle 82 To the air discharge port 8 there is connected a nozzle 82 via a flexible tube 81.
  • a course keeper 83 can put the course in good condition by injecting a part of the cold air from the cold air supply tube 55b through the nozzle 82 via the air discharge port 8 and the flexible tube 81 thereby making up ice at an intended place of the surfaces of the course.
  • the ice making up can be carried out more effectively by injecting the cold air together with an appropriate amount of water taken from the tap water pipe 84 disposed inside the side cover 78b.
  • the course keeper 83 can skillfully put the course in good condition by utilizing the cold air injected from the nozzle 82.
  • he can spray water taken from the tap water pipe 84, freezing the sprayed water to ice fog and blowing the ice fog against a portion of the course where ice must be supplemented.
  • he can form a film of water on a portion of the course where ice must be supplemented and freezing the film of water by blowing the cold air from the nozzle 82 against the film of water.
  • an ice layer containing an appropriate amount of air which is best suitable for playing bobsleigh or luge may be formed on a surface of the course.
  • Warm water taken from the warm water pipe 80 may be utilized to melt ice on an intended portion of the course and to melt snow on an intended portion of the facility. For example, snow fallen and accumulated on the passage 54 of Fig. 9 may be melted away by the warm water so that a truck may readily run on the passage to transport vehicles from the finish point to the start point.
  • a course for playing bobsleigh or luge is snaky in various directions, the required cooling capacity greatly differs from portion to portion. Depending upon the direction and position, sunny or windy portions require a higher cooling capacity than other portions.
  • Such cold air injectors 86 are appropriately provided at portions of the course where increase cooling capacities are required.
  • Fig. 14 is the same as Fig. 13 except that the cold air injector 86 is substituted for the nozzle 82 of Fig. 13.
  • the same reference numerals designate the same parts.
  • Various dimensions of an ice forming equipment according to the invention in carrying out ice formation in winter in a facility for playing ice sports can be as follows: Area for ice formation in a facility: 4500 m 2 , Maximum load for ice formation of the facility: 350 kcal/hr.m 2 , Average load for ice formation of the facility: 150 kcal/hr.m 2 , Necessary rate of flow of air: 3000 m 3 /min., District and period of operation: 3 months from December to February in Japan, Average temperature of tap water: 5 °C., and Average temperature of atmospheric air: 6.4 °C.
  • the temperature of cold air supplied to the heat exchanger 4 for ice formation and the temperature of the air leaving the heat exchanger 4 for ice formation are set -45 °C, and -15 °C., respectively and the surface of the ice formed is maintained at a temperature from -1°C. to -3°C.
  • the air refrigerant ice forming equipment may be operated under the following conditions as shown in Fig. 1.
  • the air compressor 1 is operated to provide a compressed air having a temperature of 88 °C. and a pressure of 2 atmospheres.
  • the heat exchanger 2A tap water having a temperature of 5 °C. is caused pass and warmed to a temperature of the order of 60 °C
  • the heat exchanger 2B atmospheric air having a temperature of 6.4 °C, is caused pass and warmed to a temperature of the order of 40 °C.
  • the compressed air is cooled to a temperature of about 20 °C.
  • the warm water and air obtained in the heat exchangers 2A and 2B may be utilized for purposes of heating or keeping warmth in the facility.
  • the air expander 3 provides cold air having a temperature of -45 °C. and a pressure slightly higher than the atmospheric pressure (for example 1.1 atmospheres) while recovering the power of the air compressor 1.
  • the cold air is sent to the heat exchanger 4 for ice formation and utilized for forming ice under the conditions described above. Air having a temperature of -15 °C. which has left the heat exchanger 4 for ice formation is sent to the heat exchanger 5 for heat recovery where it is warmed to a temperature of 15 °C. and thereafter returned to the air compressor 1.
  • the shaft output of the heat engine 50 can be transmitted to the generator for cogeneration purpose. Furthermore, the shaft output of the heat engine 50 may be utilized as a power source for transporting passengers and goods in the facility.
  • an exhaust gas of the heat engine has a temperature of 580 °C. and a pressure of 2 atmospheres
  • an exhaust gas leaving the turbine has a temperature of 430 °C. and a pressure of 1 atmosphere
  • an exhaust gas leaving the turbine has a temperature of 250 °C. and a pressure of 1 atmosphere
  • letting the energy of the supplied fuel be 1 there will be realized an output of the shaft of about 0.25, an output of the exhaust gas turbine of about 0.1 and a heat quantity recovered in the steam and warm water of about 0.32.
  • the environment in the facility may be kept in good condition even in the severe winter season.
  • the warm water may be further utilized to melt snow in the passage 54 of Fig. 9 thereby to facilitate the transporting of vehicles from the finish point 53c to the starting points 53a, 53b.
  • the specific example described hereinabove relates to an application of the invention to a facility for playing ice sports includes a course for playing bobsleigh or luge which are played outdoor.
  • the invention is also applicable to a facility (ice rink) for playing ice skate or ice hockey which are played indoor.
  • the heat exchanger 4 for ice formation may be constructed in various variations.
  • it may be buried in the heat conducting mortar, it may be constructed in the form of a finned coil, or it may be formed in the form of a panel-type heat exchanger.
  • the refrigeration cycle of the ice forming equipment according to the invention exhibits an excellent coefficient of performance due to recovery of heat and power as described herein, in spite of the fact that air is used as a working medium. Since cold heat necessary for ice formation is obtained using air as a working medium, the ice forming equipment according to the invention is completely free from the problem of environmental pollution. To the contrary, a part of the cold air acting as a working medium can be discharged outside for a purpose of ice formation. In this case ice surfaces of an intended configuration can be readily formed. In addition, since the heat of compression of the air compressor used in making cold air can be recovered in the form of warm air and water which are in turn utilized for forming a warm environment, the power energy for operating the refrigeration cycle can be effectively recovered.
  • Construction of the equipment according to the invention in a particular facility for playing ice sports is simple and easy, since it only requires arrangement of piping for air and water.
  • the ice forming equipment constructed in a certain facility can be easily repaired.
  • comprehensive energy saving can be achieved, whereby burden of high running cost, which is a defect of existing air refrigerant ice forming equipment, can be greatly reduced.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Structural Engineering (AREA)
  • Civil Engineering (AREA)
  • Architecture (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
  • Motor Or Generator Cooling System (AREA)
  • Central Air Conditioning (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Cold Air Circulating Systems And Constructional Details In Refrigerators (AREA)
EP93906784A 1992-10-30 1993-03-17 Pneumatic ice making device Expired - Lifetime EP0667499B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP4314372A JP2546765B2 (ja) 1992-10-30 1992-10-30 氷利用施設の製氷装置
JP314372/92 1992-10-30
PCT/JP1993/000316 WO1994010515A1 (en) 1992-10-30 1993-03-17 Pneumatic ice making device

Publications (3)

Publication Number Publication Date
EP0667499A1 EP0667499A1 (en) 1995-08-16
EP0667499A4 EP0667499A4 (en) 1995-11-15
EP0667499B1 true EP0667499B1 (en) 1998-06-10

Family

ID=18052549

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93906784A Expired - Lifetime EP0667499B1 (en) 1992-10-30 1993-03-17 Pneumatic ice making device

Country Status (7)

Country Link
EP (1) EP0667499B1 (ja)
JP (1) JP2546765B2 (ja)
AT (1) ATE167279T1 (ja)
CA (1) CA2148107C (ja)
DE (1) DE69319130T2 (ja)
NO (1) NO307627B1 (ja)
WO (1) WO1994010515A1 (ja)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9409754D0 (en) * 1994-05-16 1994-07-06 Air Prod & Chem Refrigeration system
JP4172088B2 (ja) * 1999-04-30 2008-10-29 ダイキン工業株式会社 冷凍装置
WO2000077461A1 (fr) 1999-06-11 2000-12-21 Longwell Japan Co., Ltd. Dispositif de refroidissement
US9441542B2 (en) 2011-09-20 2016-09-13 General Electric Company Ultrasonic water atomization system for gas turbine inlet cooling and wet compression
RU2659696C1 (ru) * 2017-06-06 2018-07-03 Александр Андреевич Панин Воздушная турбохолодильная установка (варианты), турбодетандер и способ работы воздушной турбохолодильной установки (варианты)
EP4080137A4 (en) * 2019-12-18 2024-02-21 Univ Valencia Politecnica METHOD AND APPARATUS FOR COOLING

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US1440000A (en) * 1920-05-03 1922-12-26 Charles E Bonine Refrigeration
GB421431A (en) * 1933-03-29 1934-12-20 James Govan Improvements relating to ice rinks
GB739949A (en) * 1954-02-24 1955-11-02 Bateman Ltd E Apparatus for producing and maintaining the skating surface of ice rinks
GB890276A (en) * 1958-05-27 1962-02-28 Netzschkau Maschf Nema Improvements in or relating to cold treatment installations
FR1372024A (fr) * 1963-08-02 1964-09-11 Bertin & Cie Perfectionnements apportés à la production de neige, notamment en vue de la fabrication de pistes de ski artificielles
US3641782A (en) * 1970-06-01 1972-02-15 American Air Filter Co Ice skating rink
US3751935A (en) * 1971-12-02 1973-08-14 Calmac Manuf Corp Method and system for creating and maintaining an ice slab
US3868827A (en) * 1973-04-05 1975-03-04 Airco Inc Air cycle food freezing system and method
US3827253A (en) * 1973-04-30 1974-08-06 Burrard Refrigeration Ltd Chiller for ice rink refrigeration systems
JPS5952343B2 (ja) * 1976-02-27 1984-12-19 日立金属株式会社 熱ポンプ装置
GB1555522A (en) * 1976-08-06 1979-11-14 Normalair Garrett Ltd Environmental temperature control systems
US4123003A (en) * 1976-09-03 1978-10-31 Theodore Winston Solar energy collection panels and energy recovery systems
US4295518A (en) * 1979-06-01 1981-10-20 United Technologies Corporation Combined air cycle heat pump and refrigeration system
JPS6099969A (ja) * 1983-11-04 1985-06-03 株式会社パテイネ商会 アイスリンク冷凍機の排熱利用方式
JPH0297850A (ja) * 1988-10-03 1990-04-10 Fujikura Ltd 空気冷却器
JPH0678856B2 (ja) * 1988-10-03 1994-10-05 株式会社フジクラ 空気冷却器
JPH02116653U (ja) * 1989-03-03 1990-09-18

Also Published As

Publication number Publication date
CA2148107C (en) 2002-02-19
CA2148107A1 (en) 1994-05-11
ATE167279T1 (de) 1998-06-15
EP0667499A1 (en) 1995-08-16
JP2546765B2 (ja) 1996-10-23
NO307627B1 (no) 2000-05-02
DE69319130T2 (de) 1998-11-12
NO951653D0 (no) 1995-04-28
WO1994010515A1 (en) 1994-05-11
NO951653L (no) 1995-06-29
DE69319130D1 (de) 1998-07-16
EP0667499A4 (en) 1995-11-15
JPH06147710A (ja) 1994-05-27

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