US20070186578A1 - Air compressor and expander - Google Patents
Air compressor and expander Download PDFInfo
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- US20070186578A1 US20070186578A1 US11/704,518 US70451807A US2007186578A1 US 20070186578 A1 US20070186578 A1 US 20070186578A1 US 70451807 A US70451807 A US 70451807A US 2007186578 A1 US2007186578 A1 US 2007186578A1
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- Prior art keywords
- rotor
- air
- air compressor
- driving shaft
- driven shaft
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
- F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
- F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F01C1/16—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
- F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
- F01C11/004—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle and of complementary function, e.g. internal combustion engine with supercharger
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/06—Heating; Cooling; Heat insulation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
- F04C29/0071—Couplings between rotors and input or output shafts acting by interengaging or mating parts, i.e. positive coupling of rotor and shaft
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2230/00—Manufacture
- F04C2230/60—Assembly methods
- F04C2230/601—Adjustment
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
- F05C2225/04—PTFE [PolyTetraFluorEthylene]
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- 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
Definitions
- the present invention relates to an air compressor and expander, and more particularly, to an air compressor and expander that is capable of preventing the generation of clearance between end covers and rotors in an air cycle during which air is compressed and expanded, thereby improving refrigerating effects.
- a reverse Bryton air cycle An air cycle that is recently considered as a most effective alternative cycle is called a reverse Bryton air cycle, which uses air as refrigerant and reversely activates Bryton air cycle first developed as a gas power cycle, thereby obtaining the refrigerating effects.
- FIG. 1 is a schematic view showing the basic principle of a general air cycle
- FIG. 2 is a graph showing the relation of T-s of the general air cycle.
- an air cycle is formed wherein a compressor 1 , an expander 2 , and first and second heat exchangers 3 and 4 conduct their respective compression process ( 1 ⁇ 2 ), temperature-falling process ( 2 ⁇ 3 ), expansion process ( 3 ⁇ 4 ), and temperature-rising process ( 4 ⁇ 1 ).
- the high pressure and temperature compressed air is transmitted to outside heat source through the first heat exchanger 3 , and the temperature of air falls under constant pressure condition (under the condition where pressure is slightly dropped).
- the high temperature air transmitted to the outside heat source can be used as a heat source for heating an air conditioning space or for producing heated water.
- the air that falls at the temperature is decreased at its pressure through the expander 2 (which has a similar structure to the compressor), and the temperature of air falls to below zero.
- the heat extracted from the expander 2 is used as power for generating electricity or returns to the compressor 1 for decreasing the consumption power of the compressor 1 .
- the air that falls at the temperature and pressure is passed through the second heat exchanger 4 , such that the temperature of air rises, and at this time, since heat is absorbed from the air conditioning space, it is served for refrigeration (or freezing).
- the efficiency of the air cycle is greatly dependant upon the efficiencies of the compressor 1 and the expander 2 .
- the compressor 1 and the expander 2 have an efficiency of about 80%, so that the whole efficiency of the system is kept low.
- the isentropic efficiency of them is raised, so that the whole efficiency of the system is increased to 80% or more.
- the closing member 4 and the end cover 5 are shaft-coupled to bearings 8 , for supporting the rotation of the driving shaft 1 a and the driven shaft 2 a.
- the driving shaft 1 a if the driving shaft 1 a is rotated, the first rotor 1 coupled around the driving shaft 1 a is rotated.
- the second rotor 2 coupled around the driven shaft 2 a is rotated.
- the driving shaft 1 a and the first rotor 1 are coupled on end portions thereof by means of the fixing nut 10 and the driven shaft 2 a and the second rotor 2 are coupled on one end portions thereof by means of the fixing nut 10 , they are rotated together while the shafts are driven.
- the air flowing in through the first air flow port 3 a is compressed or expanded, while being passed through the spiral type protrusion 1 b of the first rotor 1 and the spiral type groove 2 b of the second rotor 2 , and is then discharged through the second air flow port 3 b, thereby forming the air cycle.
- oil injection type screw compressors are configured wherein the rotors are rotated in the engagement with each other and oil is supplied for sealing and cooling the screw threads on the rotors.
- the oil injection type screw compressors can not be applied to the open-air cycle where refrigerant is respired as air itself by human beings.
- the first rotor 1 and the second rotor 2 are moved up and down by the pressure variations inside the casing 3 during the rotation of the first rotor 1 and the second rotor 2 , and the gear part 6 rotating the driving shaft 1 a and the driven shaft 2 a is formed of a helical gear that is capable of reducing backlash.
- a force is generated to have the first rotor 1 and the second rotor 2 form clearances.
- the spiral type protrusion 1 b of the first rotor 1 and the spiral type groove 2 b of the second rotor 2 interfere with each other by the large clearance of the first rotor 1 and the second rotor 2 from the gear part 6 , and thus, they are abraded, such that the temperature of air is raised to decrease refrigerating efficiencies and the chips coming off from the rotors are collected and attached in a low pressure space (see FIG. 4 ).
- the gear part 6 coupled to the shafts has a protrusion 6 a adapted to abut with the inner wheels of the bearings 8 , thereby preventing the first rotor 1 and the second rotor 2 from forming a clearance from the upper side of the gear part 6 , but in a case where the rotors are rotated to the lower side of the drawing, they do not have any structure capable of preventing forming the clearance, such that the protrusion 1 b of the first rotor 1 and the groove 2 b of the second rotor 2 abut with each other.
- the upper and lower bearings 8 do not serve to sufficiently support the rotation, such that the interference between the protrusion 1 b and the groove 2 b is much generated.
- the upper bearings are formed not abutting with oil, and during the rotation of the rotors at a high speed, the heat generated from the bearings 8 is directly transmitted to the air inside the casing 3 , thereby decreasing the refrigerating performance.
- the space occupied by the air that flows to the rotors and is compressed therein is relatively smaller than a projection space of the whole rotors.
- the present invention has been made in view of the above-mentioned problems occurring in the prior art, and it is an object of the present invention to provide an air compressor and expander that is capable of having a sufficient air flow quantity to flow therein by improving the shapes of a first rotor and a second rotor and is capable of minimizing the clearance between the first and second rotors, the clearance between the rotors and a casing, and the clearance between the rotors and end covers by improving the tooth shapes of the first and second rotors, by disposing a closing cover at both end portions of a casing for housing the first rotor and the second rotors, and by disposing a clearance-preventing means at one side of the closing cover.
- an air compressor and expander including: a first rotor coupled around a driving shaft; a second rotor coupled around a driven shaft so as to operate in cooperation with the first rotor; a casing adapted to form an air compression or expansion space by the rotation of the first rotor and the second rotor; first and second end covers adapted to close the both end portions of the casing in such a manner as to have the driving shaft and the driven shaft passed therethrough in the axial direction, thereby to have the first rotor or the second rotor disposed between them; a gear part disposed on any one side of the first and second end covers in such a manner as to be coupled around the driving shaft and the driven shaft for transmitting power to the driving shaft and the driven shaft; and a clearance-preventing means disposed at the opposite side to the gear part for preventing the clearance between the end covers and the rotors.
- the clearance-preventing means is adapted to make the ends of the rotors or come into close contact with the end covers, such that the first rotor or the second rotor does not have clearance from the end covers.
- the clearance-preventing means comprises T-shaped bushings, one side of which is coupled to central portion of the rotors and the other side of which contacts with bearings supporting the rotors, and fastening members adapted to the end portions of the driving shaft and the driven shaft thereto to support the other side of the bearings for maintaining a predetermined distance between the gear part and the end cover.
- the first end cover has a rear cover formed at the outside thereof, and the second end cover has a front cover formed at the outside thereof.
- the first rotor and the second rotor are formed twisted at a predetermined twisting angle along the axial direction, and the predetermined twisting angle of the first rotor and the second rotor is within a range between 90° and 270°.
- the first rotor and the second rotor are coated with Teflon on the surfaces thereof.
- FIG. 1 is a schematic view showing the basic principle of a general air cycle
- FIG. 2 is a graph showing the relation of T-s of the general air cycle
- FIG. 3 is a sectional view showing a conventional air compressor and expander
- FIG. 4 is a perspective view showing a first rotor in the conventional air compressor and expander
- FIG. 6 is a side view showing first and second rotors of the air compressor and expander according to the first embodiment of the present invention
- FIG. 7 is a sectional view showing the air compressor and expander according to the first embodiment of the present invention.
- FIG. 8 is a sectional view taken along the line A-A of FIG. 7 ;
- FIG. 9 is a perspective view showing an air compressor and expander according to a second embodiment of the present invention.
- FIG. 10 is a side view showing first and second rotors of the air compressor and expander according to the second embodiment of the present invention.
- FIGS. 5 to 8 show an air compressor and expander according to a first embodiment of the present invention
- the air compressor and expander includes a first rotor 10 , a second rotor 20 , a casing 30 , first and second end covers 40 and 50 , a gear part 60 , and a clearance-preventing means 70 .
- the first rotor 10 is coupled around a driving shaft 11
- the second rotor 20 is coupled around a driven shaft 21 so as to operate in cooperation with the first rotor 10 .
- the first rotor 10 and the second rotor 20 have a cycloid toothed shape.
- first rotor 10 and the second rotor 20 are formed twisted at a predetermined twisting angle along the axial direction, and the predetermined twisting angle of the first rotor 10 and the second rotor 20 is within a range between 90° and 270°.
- the first rotor 10 and the second rotor 20 are coated with Teflon on the surfaces thereof.
- the casing 30 is adapted to form an air compression or expansion space by the rotation of the first rotor 10 and the second rotor 20 .
- the first and second end covers 40 and 50 are adapted to close the both end portions of the casing 30 in such a manner as to have the driving shaft 11 and the driven shaft 21 passed therethrough in the axial direction, thereby to have the first rotor 10 or the second rotor 20 disposed between them.
- An oil seal O is coupled around the driving shaft 11 and the driven shaft 21 between the first end cover 40 and the casing 30 and between the second end cover 50 and the casing 30 , for preventing oil from entering the inside of the casing 30 .
- bearings B are mounted on each of the first and second end covers 40 and 50 in such a manner as to be coupled around the driving shaft 11 and the driven shaft 21 , for supporting the rotation of the driving shaft 11 and the driven shaft 21 , and especially, at least two or more bearings B are mounted on the second end cover 50 side, for minimizing the vibration upon the high speed rotation of the driving shaft 11 and the driven shaft 21 .
- the gear part 60 is disposed on any one side of the first and second end covers 40 and 50 in such a manner as to be coupled around the driving shaft 11 and the driven shaft 21 for transmitting power to the driving shaft 11 and the driven shaft 21 , and the gear part 60 is formed of a helical gear for preventing backlash or may be formed of a high precision spur gear.
- the clearance-preventing means 70 is disposed at the opposite side to the gear part 60 for preventing clearance between the end covers 50 and the rotors 10 or 20 .
- the clearance-preventing means 70 comprises T-shaped bushings 71 , one side of which is coupled to central portion of the rotors and the other side of which contacts with bearings supporting the rotors, and fastening members 72 adapted to the end portions of the driving shaft 11 and the driven shaft 21 thereto to support the other side of the bearings for maintaining a predetermined distance between the gear part 60 and the end cover 40 .
- the gear part 60 has a protrusion 61 formed on one side thereof, for providing a predetermined distance from the bearings B coupled to the first end cover 40 .
- the gear part 60 is coupled around the driving shaft 11 and the driven shaft 21 , and at the opposite side to the gear part 60 , the first rotor 10 and the second rotor 20 are coupled inside the casing 30 by means of the clearance-preventing means 70 having the T-shaped bushings 71 , the bearings B, and the fastening members 72 , such that even though a force is generated, the first rotor 10 and the second rotor 20 do not have clearance.
- first rotor 10 and the second rotor 20 have a ring-shaped bushing 73 coupled around the driving shaft 11 and the driven shaft 21 at the sides abutting with the first end cover 40 , for completely preventing the first rotor 10 and the second rotor 20 from having the clearances from the driving shaft 11 and the driven shaft 21 .
- the gear part 60 has a rear cover 80 formed around the outside thereof, for closing the gear part 60 , and bearings B are fixed on the rear cover 80 , for supporting the driving shaft 11 and the driven shaft 21 . Moreover, an oil seal O is mounted around the driving shaft 11 passed through the rear cover 80 .
- the respective bearings B that support the gear part 60 , the driving shaft 11 and the driven shaft 21 by means of the rear cover 80 are lubricated by oil, and the oil does not enter the casing 30 by means of the oil seals O, such that only air is compressed or expanded inside the casing 30 .
- the second end cover 50 has a front cover 90 formed at the outside thereof and has a through hole 51 formed for discharging or absorbing the compressed or expanded air within the casing 30 to and from a second air flow hole 91 formed at the outside of the front cover 90 .
- the second air flow hole 91 corresponding to a first air flow hole 31 formed on one surface of the casing 30 is formed in the axial direction on the front cover 90 .
- the air compressor and expander of the present invention is used as an air compressor, the first air flow hole 31 is an air absorption hole, and the second air flow hole 91 is an air discharge hole.
- the second air flow hole 91 is an air absorption hole, and the first air flow hole 31 is an air discharge hole.
- FIGS. 9 and 10 show an air compressor and expander according to a second embodiment of the present invention.
- the air compressor and expander according to the second embodiment of the present invention has the same parts as in the first embodiment of the present invention, except that the first rotor 10 and the second rotor 20 are an involute toothed shape, and therefore, a detailed explanation on them is avoided.
- the first rotor 10 is coupled around the driving shaft 11
- the second rotor 20 is coupled around the driven shaft 21 .
- the first rotor 10 and the second rotor 20 are disposed in the casing 30 .
- first and second end covers 40 and 50 are disposed at the both end portions of the casing 30 .
- the bearings B, the oil seals O, and the ring-shaped bushings 73 are shaft-coupled at the first end cover 40 side
- the T-shaped bushings 71 , the oil seals O, and the bearings B are shaft-coupled at the second end cover 50 side, while being fixed by means of the fastening members 72 at the end portions of the driving shaft 11 and the driven shaft 21 .
- the rear cover 80 is fixed at the first end cover 40 side, and the front cover 90 is disposed at the second end cover 50 , such that air is absorbed and discharged through the second air flow port 91 formed on the front cover 90 and through the first air flow port 31 formed on the casing 30 .
- the air compressor and expander of the present invention is used as the air compressor, air is absorbed through the first air flow port 31 , i.e. an air absorption port, and the absorbed air is compressed, while being passed through the absorption space generated between the first rotor 10 and the second rotor 20 in the casing 30 during their rotation.
- the compressed air is discharged to the second air flow port 91 of the front cover 90 . i.e. the discharge port, through the through hole 51 of the second end cover 50 .
- the first rotor 10 and the second rotor 20 are fixed around the driving shaft 11 and the driven shaft 21 , so as not to generate a clearance from the driving shaft 11 and the driven shaft 21 , thereby generating no force.
- air is absorbed through the second air flow port 91 of the front cover 90 of the second end cover 50 , i.e. an air absorption port, and the absorbed air is expanded, while being passed through the absorption space generated between the first rotor 10 and the second rotor 20 in the casing 30 during their rotation.
- the expanded air is discharged to the first air flow port 31 of the casing 30 , i.e. the discharge port.
- an air compressor and expander according to the present invention that is provided with the first and second end covers disposed at the both end portions of the casing housing the first rotor and the second rotor therein and with the clearance-preventing means disposed at any one side of the first and second end covers, thereby preventing the clearance between the end covers and the rotors.
- the air compressor and expander of the present invention has a pair of air flow ports disposed in a perpendicular relation to each other, thereby minimizing the pressure drop of air.
Abstract
The present invention relates to an air compressor and expander including: a first rotor coupled around a driving shaft; a second rotor coupled around a driven shaft so as to operate in cooperation with the first rotor; a casing adapted to form an air compression or expansion space by the rotation of the first rotor and the second rotor; first and second end covers adapted to close the both end portions of the casing in such a manner as to have the driving shaft and the driven shaft passed therethrough in the axial direction, thereby to have the first rotor or the second rotor disposed between them; a gear part disposed on any one side of the first and second end covers in such a manner as to be coupled around the driving shaft and the driven shaft for transmitting power to the driving shaft and the driven shaft; and a clearance-preventing means disposed at the opposite side to the gear part for preventing the clearance between the end covers and the rotors.
Description
- 1. Field of the Invention
- The present invention relates to an air compressor and expander, and more particularly, to an air compressor and expander that is capable of preventing the generation of clearance between end covers and rotors in an air cycle during which air is compressed and expanded, thereby improving refrigerating effects.
- 2. Background of the Related Art
- As the global warming and environmental problems become severe, recently, so as to replace a refrigerant like R-134a as used up to now with new refrigerant, many endeavors for developing alternative refrigerant systems have been made by all the refrigeration companies over the world, and especially, they have studied on a new system that is environment-friendly and has a high refrigerating efficiency, without any replacement of the refrigerant itself.
- An air cycle that is recently considered as a most effective alternative cycle is called a reverse Bryton air cycle, which uses air as refrigerant and reversely activates Bryton air cycle first developed as a gas power cycle, thereby obtaining the refrigerating effects.
-
FIG. 1 is a schematic view showing the basic principle of a general air cycle, andFIG. 2 is a graph showing the relation of T-s of the general air cycle. - As shown, an air cycle is formed wherein a
compressor 1, anexpander 2, and first andsecond heat exchangers - In the compression process (1→2), air enters the
compressor 1, and after compressed therein, it is raised at pressure and temperature. - In the temperature-falling process (2→3), the high pressure and temperature compressed air is transmitted to outside heat source through the
first heat exchanger 3, and the temperature of air falls under constant pressure condition (under the condition where pressure is slightly dropped). At this time, the high temperature air transmitted to the outside heat source can be used as a heat source for heating an air conditioning space or for producing heated water. - In the expansion process (3→4), the air that falls at the temperature is decreased at its pressure through the expander 2 (which has a similar structure to the compressor), and the temperature of air falls to below zero. At this time, the heat extracted from the
expander 2 is used as power for generating electricity or returns to thecompressor 1 for decreasing the consumption power of thecompressor 1. - In the temperature-rising process (4→1), the air that falls at the temperature and pressure is passed through the
second heat exchanger 4, such that the temperature of air rises, and at this time, since heat is absorbed from the air conditioning space, it is served for refrigeration (or freezing). - The efficiency of the air cycle is greatly dependant upon the efficiencies of the
compressor 1 and theexpander 2. In the past days, thecompressor 1 and theexpander 2 have an efficiency of about 80%, so that the whole efficiency of the system is kept low. However, recently, the isentropic efficiency of them is raised, so that the whole efficiency of the system is increased to 80% or more. - In other words, when the efficiency of the
compressor 1 is low, power of thecompressor 1 is increased and the compressed temperature is raised (see the compression process (1→2) inFIG. 2 ). When the efficiency of theexpander 2 is low, the temperature of air is not sufficiently low, such that the refrigerating performance is decreased (see the expansion process (3→4) inFIG. 2 ). -
FIG. 3 is a sectional view showing a conventional air compressor and expander, andFIG. 4 is a perspective view showing a first rotor in the conventional air compressor and expander. - Hereinafter, since the air compressor and the air expander have the similar parts to each other, they will be referred to as an air compressor and expander, for the brief description of the present invention.
- As shown, the air compressor and expander includes: a
first rotor 1 coupled around adriving shaft 1 a and having aspiral type protrusion 1 b formed on the outer periphery thereof; asecond rotor 1 coupled around a drivenshaft 2 a so as to operate in cooperation with thefirst rotor 1 and having aspiral type groove 1 b corresponding to thespiral type protrusion 1 b formed on the outer periphery thereof; acasing 3 adapted to form an air compression space by the rotation of the first andsecond rotors air flow ports 3 a and 3 b formed on the both surfaces thereof in such a manner as to be disposed perpendicular to the shafts; aclosing member 4 and anend cover 5 adapted to close the both end portions of thecasing 3; agear part 6 formed on one side of theclosing member 4 in such a manner as to be coupled around thedriving shaft 1 a and the drivenshaft 2 a for transmitting power from thedriving shaft 1 a and the drivenshaft 2 a; and agear box 7 adapted to cover thegear part 6. - Also, the
closing member 4 and theend cover 5 are shaft-coupled tobearings 8, for supporting the rotation of thedriving shaft 1 a and the drivenshaft 2 a. - Further,
oil seals 9 are coupled around thefirst rotor 1 and thesecond rotor 2 sides on theclosing member 4, for preventing lubricating oil used for lubricating thegear part 6 inside thegear box 7 and thebearings 8 on theclosing member 4 from flowing to the inside of thecasing 3. - Further,
fixing nuts 10 are coupled to the other side of thegear part 6 coupled to thefirst rotor 1 and thesecond rotor 2, for fixing thefirst rotor 1 and thesecond rotor 2 to thedriving shaft 1 a and the drivenshaft 2 a. - The conventional air compressor and expander under the above configuration is disposed and driven in the air cycle.
- According to the air compressor and expander, if the
driving shaft 1 a is rotated, thefirst rotor 1 coupled around thedriving shaft 1 a is rotated. When thefirst rotor 1 is rotated, thesecond rotor 2 coupled around the drivenshaft 2 a is rotated. At this time, since thedriving shaft 1 a and thefirst rotor 1, are coupled on end portions thereof by means of thefixing nut 10 and the drivenshaft 2 a and thesecond rotor 2 are coupled on one end portions thereof by means of thefixing nut 10, they are rotated together while the shafts are driven. - Moreover, the air flowing in through the first air flow port 3 a is compressed or expanded, while being passed through the
spiral type protrusion 1 b of thefirst rotor 1 and thespiral type groove 2 b of thesecond rotor 2, and is then discharged through the secondair flow port 3 b, thereby forming the air cycle. - At this time, in case of an open-air cycle where cool air is supplied directly to an air conditioning space, refrigerant is respired as air itself by human beings, such that the air contaminated through mixing oil with pure air cannot be used. Thus, the air compressor and expander should be designed to make a clearance between the first rotor and the second rotor set to a minimum size, such that the
spiral type protrusion 1 b of thefirst rotor 1 and thespiral type groove 2 b of thesecond rotor 2 do not abut with each other. If the minimal clearance is not maintained well, the efficiencies of the compressor and the expander are decreased, thereby making the system performance and efficiency undesirably deteriorated. - By the way, most of oil injection type screw compressors are configured wherein the rotors are rotated in the engagement with each other and oil is supplied for sealing and cooling the screw threads on the rotors. However, the oil injection type screw compressors can not be applied to the open-air cycle where refrigerant is respired as air itself by human beings.
- According to the above-mentioned air compressor and expander, the
first rotor 1 and thesecond rotor 2 are moved up and down by the pressure variations inside thecasing 3 during the rotation of thefirst rotor 1 and thesecond rotor 2, and thegear part 6 rotating thedriving shaft 1 a and the drivenshaft 2 a is formed of a helical gear that is capable of reducing backlash. However, a force is generated to have thefirst rotor 1 and thesecond rotor 2 form clearances. - That is to say, the
spiral type protrusion 1 b of thefirst rotor 1 and thespiral type groove 2 b of thesecond rotor 2 interfere with each other by the large clearance of thefirst rotor 1 and thesecond rotor 2 from thegear part 6, and thus, they are abraded, such that the temperature of air is raised to decrease refrigerating efficiencies and the chips coming off from the rotors are collected and attached in a low pressure space (seeFIG. 4 ). - In more detail, in a case where the rotors are rotated to the upper side of the drawing, the
gear part 6 coupled to the shafts has aprotrusion 6 a adapted to abut with the inner wheels of thebearings 8, thereby preventing thefirst rotor 1 and thesecond rotor 2 from forming a clearance from the upper side of thegear part 6, but in a case where the rotors are rotated to the lower side of the drawing, they do not have any structure capable of preventing forming the clearance, such that theprotrusion 1 b of thefirst rotor 1 and thegroove 2 b of thesecond rotor 2 abut with each other. Especially, while the first andsecond rotors lower bearings 8 do not serve to sufficiently support the rotation, such that the interference between theprotrusion 1 b and thegroove 2 b is much generated. - Also, according to the conventional air compressor and expander, the upper bearings are formed not abutting with oil, and during the rotation of the rotors at a high speed, the heat generated from the
bearings 8 is directly transmitted to the air inside thecasing 3, thereby decreasing the refrigerating performance. - Further, according to the air compressor and expander having the
first rotor 1 with thespiral type protrusion 1 b formed thereon and thesecond rotor 2 with thespiral type groove 2 b formed thereon, undesirably, the space occupied by the air that flows to the rotors and is compressed therein is relatively smaller than a projection space of the whole rotors. - Accordingly, the present invention has been made in view of the above-mentioned problems occurring in the prior art, and it is an object of the present invention to provide an air compressor and expander that is capable of having a sufficient air flow quantity to flow therein by improving the shapes of a first rotor and a second rotor and is capable of minimizing the clearance between the first and second rotors, the clearance between the rotors and a casing, and the clearance between the rotors and end covers by improving the tooth shapes of the first and second rotors, by disposing a closing cover at both end portions of a casing for housing the first rotor and the second rotors, and by disposing a clearance-preventing means at one side of the closing cover.
- To accomplish the above object, according to the present invention, there is provided an air compressor and expander including: a first rotor coupled around a driving shaft; a second rotor coupled around a driven shaft so as to operate in cooperation with the first rotor; a casing adapted to form an air compression or expansion space by the rotation of the first rotor and the second rotor; first and second end covers adapted to close the both end portions of the casing in such a manner as to have the driving shaft and the driven shaft passed therethrough in the axial direction, thereby to have the first rotor or the second rotor disposed between them; a gear part disposed on any one side of the first and second end covers in such a manner as to be coupled around the driving shaft and the driven shaft for transmitting power to the driving shaft and the driven shaft; and a clearance-preventing means disposed at the opposite side to the gear part for preventing the clearance between the end covers and the rotors.
- The clearance-preventing means is adapted to make the ends of the rotors or come into close contact with the end covers, such that the first rotor or the second rotor does not have clearance from the end covers.
- The clearance-preventing means comprises T-shaped bushings, one side of which is coupled to central portion of the rotors and the other side of which contacts with bearings supporting the rotors, and fastening members adapted to the end portions of the driving shaft and the driven shaft thereto to support the other side of the bearings for maintaining a predetermined distance between the gear part and the end cover.
- The first end cover has a rear cover formed at the outside thereof, and the second end cover has a front cover formed at the outside thereof.
- The first rotor and the second rotor are formed twisted at a predetermined twisting angle along the axial direction, and the predetermined twisting angle of the first rotor and the second rotor is within a range between 90° and 270°.
- The first rotor and the second rotor are coated with Teflon on the surfaces thereof.
- The above and other objects, features and advantages of the present invention will be apparent from the following detailed description of the preferred embodiments of the invention in conjunction with the accompanying drawings, in which:
-
FIG. 1 is a schematic view showing the basic principle of a general air cycle; -
FIG. 2 is a graph showing the relation of T-s of the general air cycle; -
FIG. 3 is a sectional view showing a conventional air compressor and expander; -
FIG. 4 is a perspective view showing a first rotor in the conventional air compressor and expander; -
FIG. 5 is a perspective view showing an air compressor and expander according to a first embodiment of the present invention; -
FIG. 6 is a side view showing first and second rotors of the air compressor and expander according to the first embodiment of the present invention; -
FIG. 7 is a sectional view showing the air compressor and expander according to the first embodiment of the present invention; -
FIG. 8 is a sectional view taken along the line A-A ofFIG. 7 ; -
FIG. 9 is a perspective view showing an air compressor and expander according to a second embodiment of the present invention; and -
FIG. 10 is a side view showing first and second rotors of the air compressor and expander according to the second embodiment of the present invention. - Hereinafter, an explanation of an air compressor and expander according to the preferred embodiments of the present invention will be given with reference to the attached drawings.
-
FIGS. 5 to 8 show an air compressor and expander according to a first embodiment of the present invention; - As shown, the air compressor and expander according to the first embodiment of the present invention includes a
first rotor 10, asecond rotor 20, acasing 30, first and second end covers 40 and 50, agear part 60, and a clearance-preventingmeans 70. - The
first rotor 10 is coupled around a drivingshaft 11, and thesecond rotor 20 is coupled around a drivenshaft 21 so as to operate in cooperation with thefirst rotor 10. In this case, thefirst rotor 10 and thesecond rotor 20 have a cycloid toothed shape. - Moreover, the
first rotor 10 and thesecond rotor 20 are formed twisted at a predetermined twisting angle along the axial direction, and the predetermined twisting angle of thefirst rotor 10 and thesecond rotor 20 is within a range between 90° and 270°. Desirably, thefirst rotor 10 and thesecond rotor 20 are coated with Teflon on the surfaces thereof. - The
casing 30 is adapted to form an air compression or expansion space by the rotation of thefirst rotor 10 and thesecond rotor 20. - The first and second end covers 40 and 50 are adapted to close the both end portions of the
casing 30 in such a manner as to have the drivingshaft 11 and the drivenshaft 21 passed therethrough in the axial direction, thereby to have thefirst rotor 10 or thesecond rotor 20 disposed between them. - An oil seal O is coupled around the driving
shaft 11 and the drivenshaft 21 between thefirst end cover 40 and thecasing 30 and between thesecond end cover 50 and thecasing 30, for preventing oil from entering the inside of thecasing 30. - Further, bearings B are mounted on each of the first and second end covers 40 and 50 in such a manner as to be coupled around the driving
shaft 11 and the drivenshaft 21, for supporting the rotation of the drivingshaft 11 and the drivenshaft 21, and especially, at least two or more bearings B are mounted on thesecond end cover 50 side, for minimizing the vibration upon the high speed rotation of the drivingshaft 11 and the drivenshaft 21. - The
gear part 60 is disposed on any one side of the first and second end covers 40 and 50 in such a manner as to be coupled around the drivingshaft 11 and the drivenshaft 21 for transmitting power to the drivingshaft 11 and the drivenshaft 21, and thegear part 60 is formed of a helical gear for preventing backlash or may be formed of a high precision spur gear. - The clearance-preventing
means 70 is disposed at the opposite side to thegear part 60 for preventing clearance between the end covers 50 and therotors means 70 comprises T-shaped bushings 71, one side of which is coupled to central portion of the rotors and the other side of which contacts with bearings supporting the rotors, andfastening members 72 adapted to the end portions of the drivingshaft 11 and the drivenshaft 21 thereto to support the other side of the bearings for maintaining a predetermined distance between thegear part 60 and theend cover 40. - The
gear part 60 has a protrusion 61 formed on one side thereof, for providing a predetermined distance from the bearings B coupled to thefirst end cover 40. - That is to say, at the state where the protrusion 61 of the
gear part 60 is spaced apart from the bearings B of thefirst end cover 40 by a predetermined distance, thegear part 60 is coupled around the drivingshaft 11 and the drivenshaft 21, and at the opposite side to thegear part 60, thefirst rotor 10 and thesecond rotor 20 are coupled inside thecasing 30 by means of the clearance-preventingmeans 70 having the T-shaped bushings 71, the bearings B, and thefastening members 72, such that even though a force is generated, thefirst rotor 10 and thesecond rotor 20 do not have clearance. - On the other hand, the
first rotor 10 and thesecond rotor 20 have a ring-shapedbushing 73 coupled around the drivingshaft 11 and the drivenshaft 21 at the sides abutting with thefirst end cover 40, for completely preventing thefirst rotor 10 and thesecond rotor 20 from having the clearances from the drivingshaft 11 and the drivenshaft 21. - The
gear part 60 has arear cover 80 formed around the outside thereof, for closing thegear part 60, and bearings B are fixed on therear cover 80, for supporting the drivingshaft 11 and the drivenshaft 21. Moreover, an oil seal O is mounted around the drivingshaft 11 passed through therear cover 80. - The respective bearings B that support the
gear part 60, the drivingshaft 11 and the drivenshaft 21 by means of therear cover 80 are lubricated by oil, and the oil does not enter thecasing 30 by means of the oil seals O, such that only air is compressed or expanded inside thecasing 30. - Further, the
second end cover 50 has afront cover 90 formed at the outside thereof and has a through hole 51 formed for discharging or absorbing the compressed or expanded air within thecasing 30 to and from a secondair flow hole 91 formed at the outside of thefront cover 90. - In other words, the second
air flow hole 91 corresponding to a first air flow hole 31 formed on one surface of thecasing 30 is formed in the axial direction on thefront cover 90. - In this case, if the air compressor and expander of the present invention is used as an air compressor, the first air flow hole 31 is an air absorption hole, and the second
air flow hole 91 is an air discharge hole. To the contrary, if used as an air expander, the secondair flow hole 91 is an air absorption hole, and the first air flow hole 31 is an air discharge hole. -
FIGS. 9 and 10 show an air compressor and expander according to a second embodiment of the present invention. - As shown, the air compressor and expander according to the second embodiment of the present invention has the same parts as in the first embodiment of the present invention, except that the
first rotor 10 and thesecond rotor 20 are an involute toothed shape, and therefore, a detailed explanation on them is avoided. - Now, an explanation of the operation of the air compressor and expander according to the preferred embodiment of the present invention will be in detail given.
- The
first rotor 10 is coupled around the drivingshaft 11, and thesecond rotor 20 is coupled around the drivenshaft 21. After that, thefirst rotor 10 and thesecond rotor 20 are disposed in thecasing 30. - Also, the first and second end covers 40 and 50 are disposed at the both end portions of the
casing 30. In this case, the bearings B, the oil seals O, and the ring-shapedbushings 73 are shaft-coupled at thefirst end cover 40 side, and the T-shaped bushings 71, the oil seals O, and the bearings B are shaft-coupled at thesecond end cover 50 side, while being fixed by means of thefastening members 72 at the end portions of the drivingshaft 11 and the drivenshaft 21. - The
first rotor 10 and thesecond rotor 20, which are coupled around the drivingshaft 11 and the drivenshaft 21 and are disposed inside thecasing 30, are supported at one sides thereof by means of the bearings B of thegear part 60 and are fixed at the other sides thereof by means of the clearance-preventingmeans 70, i.e. the T-shaped bushings 71, the bearings B and thefastening members 72, such that as thefirst rotor 10 and thesecond rotor 20 do not interfere with each other, they are not abraded, thereby improving the refrigeration capability. - Also, the
rear cover 80 is fixed at thefirst end cover 40 side, and thefront cover 90 is disposed at thesecond end cover 50, such that air is absorbed and discharged through the secondair flow port 91 formed on thefront cover 90 and through the first air flow port 31 formed on thecasing 30. - Referring to the air flow when the air compressor and expander of the present invention is used as the air compressor, air is absorbed through the first air flow port 31, i.e. an air absorption port, and the absorbed air is compressed, while being passed through the absorption space generated between the
first rotor 10 and thesecond rotor 20 in thecasing 30 during their rotation. Next, the compressed air is discharged to the secondair flow port 91 of thefront cover 90. i.e. the discharge port, through the through hole 51 of thesecond end cover 50. - In this process, the
first rotor 10 and thesecond rotor 20 are fixed around the drivingshaft 11 and the drivenshaft 21, so as not to generate a clearance from the drivingshaft 11 and the drivenshaft 21, thereby generating no force. - Referring to the air flow when the air compressor and expander of the present invention is used as the air expander, air is absorbed through the second
air flow port 91 of thefront cover 90 of thesecond end cover 50, i.e. an air absorption port, and the absorbed air is expanded, while being passed through the absorption space generated between thefirst rotor 10 and thesecond rotor 20 in thecasing 30 during their rotation. Next, the expanded air is discharged to the first air flow port 31 of thecasing 30, i.e. the discharge port. - As described above, there is provided an air compressor and expander according to the present invention that is provided with the first and second end covers disposed at the both end portions of the casing housing the first rotor and the second rotor therein and with the clearance-preventing means disposed at any one side of the first and second end covers, thereby preventing the clearance between the end covers and the rotors.
- Additionally, the air compressor and expander of the present invention has a pair of air flow ports disposed in a perpendicular relation to each other, thereby minimizing the pressure drop of air.
- While the present invention has been described with reference to the particular illustrative embodiments, it is not to be restricted by the embodiments but only by the appended claims. It is to be appreciated that those skilled in the art can change or modify the embodiments without departing from the scope and spirit of the present invention.
Claims (8)
1-7. (canceled)
8. An air compressor and expander comprising:
a first rotor coupled around a driving shaft;
a second rotor coupled around a driven shaft so as to operate in cooperation with the first rotor;
a casing adapted to form an air compression or expansion space by the rotation of the first rotor and the second rotor;
first and second end covers adapted to close the both end portions of the casing in such a manner as to have the driving shaft and the driven shaft passed therethrough in the axial direction, thereby to have the first rotor or the second rotor disposed between them;
a gear part disposed on any one side of the first and second end covers in such a manner as to be coupled around the driving shaft and the driven shaft for transmitting power to the driving shaft and the driven shaft; and
a clearance-preventing means disposed at the opposite side to the gear part for preventing clearance between the end covers and the rotors.
9. The air compressor and expander according to claim 8 , wherein the clearance-preventing means is adapted to make the ends of the rotors come into close contact with the end covers, such that the first rotor or the second rotor does not have clearance from the end covers.
10. The air compressor and expander according to claim 8 , wherein the clearance-preventing means comprises T-shaped bushings, one side of which is coupled to central portion of the rotors and the other side of which contacts with bearings supporting the rotors, and fastening members adapted to the end portions of the driving shaft and the driven shaft thereto to support the other side of the bearings for maintaining a predetermined distance between the gear part and the end cover.
11. The air compressor and expander according to claim 8 , wherein the first end cover has a rear cover formed at the outside thereof, and the second end cover has a front cover formed at the outside thereof.
12. The air compressor and expander according to claim 8 , wherein the first rotor and the second rotor are formed twisted at a predetermined twisting angle along the axial direction, and the predetermined twisting angle of the first rotor and the second rotor is within a range between 90° and 270°.
13. The air compressor and expander according to claim 9 , wherein the first rotor and the second rotor are formed twisted at a predetermined twisting angle along the axial direction, and the predetermined twisting angle of the first rotor and the second rotor is within a range between 90° and 270°.
14. The air compressor and expander according to claim 8 , wherein the first rotor and the second rotor are coated with Teflon on the surfaces thereof.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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KR10-2006-0013734 | 2006-02-13 | ||
KR1020060013734A KR101207298B1 (en) | 2006-02-13 | 2006-02-13 | air compressor and expander |
Publications (1)
Publication Number | Publication Date |
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US20070186578A1 true US20070186578A1 (en) | 2007-08-16 |
Family
ID=38366903
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/704,518 Abandoned US20070186578A1 (en) | 2006-02-13 | 2007-02-09 | Air compressor and expander |
Country Status (2)
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US (1) | US20070186578A1 (en) |
KR (1) | KR101207298B1 (en) |
Cited By (5)
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US20110146337A1 (en) * | 2009-12-22 | 2011-06-23 | Nissan Technical Center North America, Inc. | Air conditioning system |
US20180087509A1 (en) * | 2015-04-06 | 2018-03-29 | Trane International Inc. | Active clearance management in screw compressor |
CN108036536A (en) * | 2017-11-02 | 2018-05-15 | 李落成 | A kind of air-conditioning refrigeration system |
WO2018189043A1 (en) * | 2017-04-11 | 2018-10-18 | Gardner Denver Schopfheim Gmbh | Screw-type compressor arrangement having an axial bearing and a radial bearing |
WO2021026599A1 (en) * | 2019-08-09 | 2021-02-18 | Eric Davies | Gas-cycle system for heating or cooling |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
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CN112746958B (en) * | 2021-01-04 | 2022-07-12 | 西安交通大学 | Double-screw compression and expansion integrated machine for fuel cell |
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US4253713A (en) * | 1979-10-22 | 1981-03-03 | Disposable Waste Systems, Inc. | High integrity fluid pressure rotary shaft seal |
US4693813A (en) * | 1985-07-30 | 1987-09-15 | Toyota Jidosha Kabushiki Kaisha | Method of broaching outer periphery of lobe-type rotor of roots-type fluid machine, and broaching cutter used in the method |
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US20110146337A1 (en) * | 2009-12-22 | 2011-06-23 | Nissan Technical Center North America, Inc. | Air conditioning system |
US20180087509A1 (en) * | 2015-04-06 | 2018-03-29 | Trane International Inc. | Active clearance management in screw compressor |
US10539137B2 (en) * | 2015-04-06 | 2020-01-21 | Trane International Inc. | Active clearance management in screw compressor |
US10738781B2 (en) | 2015-04-06 | 2020-08-11 | Trane International Inc. | Active clearance management in screw compressor |
WO2018189043A1 (en) * | 2017-04-11 | 2018-10-18 | Gardner Denver Schopfheim Gmbh | Screw-type compressor arrangement having an axial bearing and a radial bearing |
CN108036536A (en) * | 2017-11-02 | 2018-05-15 | 李落成 | A kind of air-conditioning refrigeration system |
WO2021026599A1 (en) * | 2019-08-09 | 2021-02-18 | Eric Davies | Gas-cycle system for heating or cooling |
US11939870B2 (en) | 2019-08-09 | 2024-03-26 | Eric Davies | Gas-cycle system for heating or cooling |
Also Published As
Publication number | Publication date |
---|---|
KR101207298B1 (en) | 2012-12-03 |
KR20070081636A (en) | 2007-08-17 |
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Legal Events
Date | Code | Title | Description |
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AS | Assignment |
Owner name: HALLA CLIMATE CONTROL CORPORATION, KOREA, REPUBLIC Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:LEE, JUNKANG;REEL/FRAME:019108/0433 Effective date: 20070125 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |