| 序号 | 专利名 | 申请号 | 申请日 | 公开（公告）号 | 公开（公告）日 | 发明人 |
|---|---|---|---|---|---|---|
| 201 | Multistage compression refrigerating machine for supplying refrigerant from subcooler to cool rotating machine and lubricating oil | US09904891 | 2001-07-16 | US06460371B2 | 2002-10-08 | Akihiro Kawada |
| A multistage compression refrigerating machine is disclosed, which efficiently cools a rotating machine such as an electric motor and lubricating oil by using a refrigerant and increases the amount of refrigerant to be used to provide the refrigerating capacity in the evaporator, thereby improving the refrigerating capacity. The machine comprises a condenser for supplying a condensed refrigerant to an evaporator via a subcooler: a multistage compression system for absorbing the above refrigerant, absorbing a refrigerant evaporated from the subcooler, from an intermediate position between adjacent compressors, compressing the absorbed refrigerants together, and discharging it to the condenser; a rotating-machine cooler for cooling a rotating machine for driving the multistage compression system; and a lubricating-oil cooler for cooling lubricating oil. The refrigerant extracted from the subcooler is supplied to the rotating-machine cooler and the lubricating-oil cooler, and this refrigerant is returned to the evaporator after cooling. | ||||||
| 202 | Compressor economizer circuit with check valve | US09447481 | 1999-11-23 | US06202438B1 | 2001-03-20 | Thomas Barito |
| An improved efficiency economizer system for compressors incorporates the use of a check valve blocking return flow into the economizer return line. The economizer return line communicates with an economizer port, which communicates with a compression chamber. Pressure in the compression chamber can vary during the operational cycle of the compressor. Thus, in the past, there has sometimes been backflow of refrigerant through the economizer injection port and into the return line. The present invention prevents this backflow. Most preferably, the invention is utilized on scroll compressors; however, other types of compressors may benefit from this invention. | ||||||
| 203 | Apparatus and methods for cooling and sealing rotary helical screw compressors | US323584 | 1994-10-17 | US5653585A | 1997-08-05 | Anthony N. Fresco |
| In a compression system which incorporates a rotary helical screw compressor, and for any type of gas or refrigerant, the working liquid oil is atomized through nozzles suspended in, and parallel to, the suction gas flow, or alternatively the nozzles are mounted on the suction piping. In either case, the aim is to create positively a homogeneous mixture of oil droplets to maximize the effectiveness of the working liquid oil in improving the isothermal and volumetric efficiencies. The oil stream to be atomized may first be degassed at compressor discharge pressure by heating within a pressure vessel and recovering the energy added by using the outgoing oil stream to heat the incoming oil stream. The stripped gas is typically returned to the compressor discharge flow. In the preferred case, the compressor rotors both contain a hollow cavity through which working liquid oil is injected into channels along the edges of the rotors, thereby forming a continuous and positive seal between the rotor edges and the compressor casing. In the alternative method, working liquid oil is injected either in the same direction as the rotor rotation or counter to rotor rotation through channels in the compressor casing which are tangential to the rotor edges and parallel to the rotor centerlines or alternatively the channel paths coincide with the helical path of the rotor edges. | ||||||
| 204 | Apparatus and method of oil charge loss protection for compressors | US266539 | 1994-06-27 | US5431025A | 1995-07-11 | Robert L. Oltman; Michael D. Carey |
| A method of compressor over temperature protection. The method comprises the steps of monitoring the temperature of oil entering a compressor, determining an oil temperature differential between the entering and exiting oil temperatures, comparing the oil temperature differential to first and second predetermined limits, terminating compressor operation if the first limit is exceeded by the oil temperature differential, and terminating compressor operation if the second temperature limit is exceeded by the oil temperature differential for longer than a first time period. | ||||||
| 205 | Scroll compressor oil circulation system | US147115 | 1993-11-03 | US5370513A | 1994-12-06 | Gary K. Fain |
| A scroll compressor oil circulation system has the usual concentric bore oil pump which supplies lubricating oil to a chamber within which an impeller rotates. The rotating of the impeller within this chamber pumps lubricating oil through a passage which communicates with a control passage which injects a quantity of lubricant into the compression chambers of the scrolls for cooling and lubrication. The amount of oil injected into the compression chamber is controlled by the shape of the control passage through the orbiting scroll. | ||||||
| 206 | Lubricated rotary compressor having a cooling medium inlet to the delivery port | US57411 | 1993-05-06 | US5273412A | 1993-12-28 | Marianus H. J. M. Zwaans |
| A rotary compressor such as a screw-type or a spiral compressor comprises a compressor stator and one or more rotary compression elements, which compressor stator is provided with a suction port, a delivery port and a lubricant inlet, the lubricant being intended for lubricating each compression element, for sealing the gaps between the individual compression elements and between the compression elements and the compressor stator, and for cooling the medium to be compressed during the compression process. The compressor also comprises an inlet for a cooling medium for cooling the lubricant which opens out near or in the delivery port. | ||||||
| 207 | Scroll type fluid machine having intermittent oil feed to working chamber | US897384 | 1992-06-12 | US5249941A | 1993-10-05 | Yoshitaka Shibamoto |
| A scroll type fluid machine is provided with a mechanism for injecting oil into fluid working chambers such that a precise amount of oil is supplied without using any capillary tube, instead using intermittent oil feed from an oil sump through a communicating passage into the working chambers. Within a sealed casing, a first scroll having a spiral ridge and a second scroll having a spiral ridge are interleaved forming working chambers therebetween. A precise amount of oil is supplied to the working chambers from an oil sump which is in flow communication with an oil feed chamber provided on the end face of a cylinder member which is in sliding contact with the end plate of the second scroll. The oil feed chamber is in intermittent flow communication with a communicating passage which intermittently connects the oil feed chamber to the working chambers as the second scroll revolves. | ||||||
| 208 | Scroll compressor with swirling impeller biased by cooled lubricant | US720456 | 1991-09-03 | US5217360A | 1993-06-08 | Sadao Kawahara; Michio Yamamura; Jiro Yuda; Yoshinori Kojima; Shuichi Yamamoto; Manabu Sakai; Shigeru Muramatsu; Osamu Aiba |
| A swirling spiral impeller portion 13 is structured such that a pressure between the suction and discharge pressures acts on a part of the rear surface thereof. The compressor includes a means for adjusting and cooling the intermediate pressure which acts on a part of the swirling spiral impeller portion 13 by means of the lubricant oil stored in a lubricant oil reservoir 26 to which the discharge pressure in the sealed container acts. The lubricant oil supplied to the compression portion is provided under any pressure condition, and is always supplied stably. As the lubricant oil is cooled, it does not reduce the efficiency greatly. | ||||||
| 209 | Twin shaft vacuum pump with purge gas inlet | US481853 | 1990-02-20 | US5046934A | 1991-09-10 | Hanns-Peter Berges |
| A twin-shaft vacuum pump including a rotor pair mounted for rotation in a pump chamber. The rotor pair together with the chamber wall define a suction side and delivery side of the pump chamber. In order to prevent solid particles suspended in pump fluid from settling in the chamber, the invention provides a flushing gas outlet orifice disposed on the delivery side of the pump chamber and adapted to be connected to a source of flushing gas. The solid particles can thus be held in suspension and conveyed from the pump with the assistance of flushing gas supplied through the orifice. | ||||||
| 210 | Centrifugal scavenging system for single screw compressors | US885480 | 1986-07-03 | US4775304A | 1988-10-04 | Thomas W. Bein |
| A scavenging system for single screw compressors to remove residual liquideal from an open combustion chamber prior to controlled liquid seal injection. The removal of residual liquid seal is accomplished by providing the casing with a scavenging slot which surrounds a portion of the open combustion chamber thereby allowing centrifugal force to radially remove residual liquid seal. | ||||||
| 211 | Regulator for cooling or heat pump systems | US935218 | 1986-11-26 | US4720250A | 1988-01-19 | Rune Glanvall |
| A rotary compressor in a cooling or a heat pump system which is provided with an oil injector and includes an oil separator on the high pressure side of the system. Oil is returned to the compressor for lubrication, cooling and sealing and is normally caused to circulate by means of the natural pressure differences in the cooling system. When the pressure level is too small to provide sufficient oil circulation, an oil pump is connected. By employing a pressure controlled regulating valve in the system, which serves both as a pressure regulating and a flow regulating valve, the oil pump may be caused to run idle when a sufficient pressure difference has been attained in the system. | ||||||
| 212 | Compressor-scavenging eductor system | US759567 | 1985-07-26 | US4655698A | 1987-04-07 | David C. Winyard |
| The present invention overcomes performance losses of positive displacement compressors due to internal liquid recirculation. This is achieved by removing or scavenging liquid that leaks out of the compression pocket before it is captured by another lower-pressure compression pocket of the compressor. The scavenged liquid is collected in the bottom of the compressor pressure vessel and cooled before it is reinjected into the compressor to complete the cycle. | ||||||
| 213 | Method of operation for an oil-injected screw-compressor | US694125 | 1985-01-22 | USRE32055E | 1985-12-24 | (Lars) Lauritz B. Schibbye; Rolf A. Englund |
| This invention relates to a method at oil-injected screw-compressors for balancing axial forces at at least one of the rotors of the compressor, for sealing the gaps between rotor housing and rotor shafts and for cooling and lubricating the bearings of the rotor shafts. At the high-pressure end of the compressor oil under pressure of such magnitude is supplied to the bearing spaces (28a,28b) at the ends of both rotors that an oil flow inward to the compression space along the gaps (32a,32b) between the rotor shafts and the rotor housing is obtained for sealing against leakage from the compression space. Oil at this pressure further is supplied via a connection (42) from the bearing space (28b) of the female rotor to a pressure space (38) at the low-pressure end of the female rotor for balancing the axial force arising on the shaft end (31) of the female rotor on the high-pressure side due to the oil supplied to the bearing space (28b) of the female rotor. | ||||||
| 214 | Closed loop compressed gas system with oil mist lubricated screw compressor | US193496 | 1980-10-03 | US4375156A | 1983-03-01 | David N. Shaw |
| A rotary helical screw compressor for a refrigeration system employing a condensable refrigerant comprises intermeshed rotors mounted for rotation by way of anti-friction bearings, within a hermetic housing. A lubricating oil miscible in liquid refrigerant is supplied to the compressor in a mass ratio of between 0.25 and 12%, by weight of solution. Vaporized working fluid at discharge pressure and bearing oil mist is permitted to seep through the anti-friction bearings in closed loops, from the discharge side of the machine towards the suction side, for effective lubrication. Thus, the refrigeration system is oil pump free, oil sump free, and oil filter free. Liquid refrigerant oil solution may be bled from the condenser and injected into the compression chamber defined partially by the intermeshed rotors at a point in the compression process where the compression chamber is cut off from suction and discharge sides of the compressor, for cooling the rotors. | ||||||
| 215 | Blade-type rotary compressor with full unloading and oil sealed interfaces | US704886 | 1976-07-13 | US4068981A | 1978-01-17 | Zoltan A. Mandy |
| A rotary compressor apparatus having a housing with a rotor eccentrically mounted therein and such rotor includes a plurality of sliding vanes which define constantly changing compression pockets as the rotor is rotated. The apparatus includes a plurality of ports which may be opened to permit full unloading when starting the compressor and which may be selectively closed to control the quantity of gaseous matter being compressed. The apparatus also includes a high pressure oil injector at each end of the rotor for sealing such ends to prevent loss of compression. | ||||||
| 216 | Refrigerating apparatus | US699090 | 1976-06-23 | US4062199A | 1977-12-13 | Keisuke Kasahara; Sachio Hamaoka; Youichi Katori; Takaharu Mizuno |
| A refrigerating apparatus comprising a refrigerating cycle into which a screw compressor is incorporated, and a liquid super cooler connected on the way of a liquid pipe of said refrigerating cycle, said screw compressor having a gas intake and/or liquid coolant injection opening which is located at a position where the screw blades of the screw compressor have at least partially compressed the gas in the screw compressor. The position of the gas intake provided in the screw compressor and intended to pass the gas from the liquid super cooler into the screw compressor is limited under such a condition thatV.sub.i = 1.0 .about. 4.5In which ##EQU1## V.sub.L represents the theoretically maximum screw space volume (m.sup.3 /h) in the screw compressor and V.sub.H represents the screw space volume (m.sup.3 /h) at the position of the gas intake. The position of the liquid injection opening provided in the screw compressor and intended to pass the liquid coolant into the screw compressor is limited under such a condition thatV.sub.i = 1.0 .about. 3.7In which ##EQU2## V.sub.L represents the theoretically maximum screw space volume (m.sup.3 /h) in the screw compressor and V.sub.H represents the screw space volume (m.sup.3 /h) at the position of the liquid coolant injection opening. | ||||||
| 217 | Compression systems and compressors | US527104 | 1974-11-25 | US4020642A | 1977-05-03 | Geoffrey Gordon Haselden; Guy Francis Hundy |
| In a gas compression system employing a positive-displacement rotary compressor, liquid is injected into the compressor which is the liquid phase of the gas or vapour being compressed and the compressor temperatures are maintained at about the saturation temperatures of the gas or vapour. The quantity of liquid injected is sufficient to fill, at least partially, the internal compressor clearance gaps. An electric driving motor is contained with the compressor in another chamber of the same of casing and the motor windings are cooled by being bathed in the wet gas mixture leaving the compressor discharge. | ||||||
| 218 | Oil-injection-type rotary compressor having a centrifugal water separator | US425994 | 1973-12-19 | US3945464A | 1976-03-23 | Goro Sato |
| An oil-injection-type rotary compressor having a centrifugal water separator which is disposed in the cooling and lubricating oil system thereof, and which is characterized in that water particles contained in the cooling and lubricating oil are automatically separated either continuously or intermittently from the lubricating oil and are discharged therefrom to the exterior of the compressor. | ||||||
| 219 | Refrigerant screw compression with liquid refrigerant injection | US380115 | 1973-07-17 | US3931718A | 1976-01-13 | Geoffrey Gordon Haselden |
| A screw compressor, compressing refrigerant gas in a refrigeration system, which has liquid refrigerant passed back through it, in counter flow to the gas being compressed, for sealing the rotor clearances. The liquefied gas from the condenser of the system returns to the evaporator either wholly by way of the compressor or partly by way of the compressor as aforesaid and partly through a bypass equipped with an expansion valve. | ||||||
| 220 | Air conditioning system having reduced driving requirement | US46584174 | 1974-05-01 | US3913351A | 1975-10-21 | EDWARDS THOMAS C |
| An air conditioning unit having a driven rotor with a plurality of vanes and defining a compressor portion and an expander portion, each having inlet and outlet ports, with a first heat exchanger connected between the compressor outlet port and the expander inlet port. A non-condensing gas such as air is fed into the compressor inlet port, compressed, cooled by the heat exchanger, and expanded back to substantially its initial pressure for discharge in the cold state at the expander outlet port, a non-condensing gas being defined as any gas which does not condense at the pressures and temperatures encountered in the unit. In accordance with the main feature of the present invention, means are provided for causing the non-condensing gas, as it enters the inlet port of the compressor, to be substantially saturated with a condensible additive fluid, having a high heat of vaporization and which condenses within the range of temperature achieved in the expander thereby to release heat of vaporization in the expander resulting in an increase in the work of expansion to reduce the net work required to drive the rotor. In one embodiment of the invention the system is open and air is used as gas, with water as the additive. In such embodiment the cold air is directly to the cooled space. In a second embodiment a second heat exchanger is connected between the expander outlet port and the compressor inlet port to form a closed loop sealed against escape of gas. When the system is closed, the gas and additive fluid may take many different forms, and a lubricant may be included to lubricate the vanes of the rotor.
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