EP2863060B2 - Screw Compressor and oil supply method thereof - Google Patents

Screw Compressor and oil supply method thereof Download PDF

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Publication number
EP2863060B2
EP2863060B2 EP14181227.1A EP14181227A EP2863060B2 EP 2863060 B2 EP2863060 B2 EP 2863060B2 EP 14181227 A EP14181227 A EP 14181227A EP 2863060 B2 EP2863060 B2 EP 2863060B2
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EP
European Patent Office
Prior art keywords
oil
rotor
supply line
oil supply
tooth groove
Prior art date
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Active
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EP14181227.1A
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German (de)
English (en)
French (fr)
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EP2863060A1 (en
EP2863060B1 (en
Inventor
Takanori Imashiro
Toshiyuki Miyatake
Hiromu Yamazaki
Shoji Yoshimura
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Kobe Steel Ltd
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Kobe Steel Ltd
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Classifications

    • 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
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow

Definitions

  • the present invention relates to an oil cooling type screw compressor
  • Such a compressor is disclosed in JP9-303279 .
  • a secondary separation is performed by a filter in addition to a primary separation performed by a centrifugal force inside an oil collector in order to separate an oil included in an air discharged from a compressor body (see JP 2013-36397 A ).
  • the oil separated by the secondary separation is collected and is returned to a system, the oil is directly returned to a suction port of a main body or a tooth groove of each rotor being in the course of compression and having a pressure lower than the secondarily separated oil in many cases.
  • the returned oil includes a large amount of hot-temperature air, volume efficiency is degraded when the oil is directly returned to the suction port, and a power necessary for driving the compressor increases when the oil is directly returned to the tooth groove being in the course of compression.
  • the present invention is made in view of the above-described problems, and an object thereof is to provide a compressor capable of decreasing a power necessary for a driving operation
  • a compressor according to claim 1 including: a compressor body that includes a suction port which suctions a gas, a pair of rotors comprising a female rotor and a male rotor which are rotatably supported by a bearing and compressing the gas suctioned from the suction port in cooperation with a rotor chamber, and an discharge port which discharges the compressed gas; an oil collector that includes a primary separation unit which primarily separates an oil from the gas compressed by the compressor body and a secondary separation unit which secondarily separates an oil from the gas from which the oil is primarily separated by the primary separation unit; a primary separation oil supply line that is connected to a compression tooth groove space of the female rotor defined by an inner wall of the rotor chamber and a pair of adjacent teeth of the female rotor in a cross-section perpendicular to a rotor shaft of the compressor body, and to the oil collector, the primary separation oil supply line supplying the oil separated by the primary separation unit
  • a fluid mixture of the oil and the gas passes through the secondary separation oil supply line.
  • the secondary separation oil supply line is connected to the primary separation oil supply line, the fluid mixture of the primarily separated oil and the pressurized gas is supplied to the compression tooth groove space of the female rotor.
  • the dispersion of the oil is promoted, and hence the deflection of the oil hardly occurs in the tooth groove of the female rotor.
  • oil shortage is prevented between the inner wall of the rotor chamber and the tooth tip of the female rotor as the seal portion where particularly partial oil shortage easily occurs, and hence a back flow in which the gas in the course of compression leaks therebetween may be prevented.
  • the power necessary for driving the rotor in order to compress the leakage gas again decreases, and hence the amount of the air discharged from the compressor body may be also increased.
  • the fluid mixture is released to the compression tooth groove space of the female rotor, the atomization of the oil is promoted, and hence the surface area of the oil with respect to the amount of the oil supplied to the female rotor increases.
  • heat is easily exchanged between the oil supplied to the compressor body and the gas in the course of compression. Accordingly, since the efficiency of the cooling process using the oil is improved, the gas almost becomes an isothermal compression state, and hence the power for driving the female rotor decreases.
  • the tooth tip width of the tooth of the female rotor is generally narrow, and the amount of the gas leaking between the tooth tip of the female rotor and the compressor body is easily affected by the existence of the oil therebetween.
  • the volume of the tooth groove of the female rotor is larger than that of the male rotor, it is considered that the merit in which the fluid mixture is supplied to the compression tooth groove space of the female rotor is larger than that of the case where the fluid mixture is supplied to the male rotor.
  • the primary separation oil supply line may be further connected to a compression tooth groove space of the male rotor defined by the inner wall of the rotor chamber and a pair of adjacent teeth of the male rotor in a cross-section perpendicular to the rotor shaft of the compressor body and may supply the oil which is separated by the primary separation unit and does not include the oil passing through the secondary separation oil supply line to the compression tooth groove space of the male rotor.
  • the compressor may further include another primary separation oil supply line for the male rotor that is connected to a compression tooth groove space of the male rotor defined by the inner wall of the rotor chamber and a pair of adjacent teeth of the male rotor in a cross-section perpendicular to the rotor shaft of the compressor body and the oil collector and supplies the oil separated by the primary separation unit to the compression tooth groove space of the male rotor.
  • another primary separation oil supply line for the male rotor that is connected to a compression tooth groove space of the male rotor defined by the inner wall of the rotor chamber and a pair of adjacent teeth of the male rotor in a cross-section perpendicular to the rotor shaft of the compressor body and the oil collector and supplies the oil separated by the primary separation unit to the compression tooth groove space of the male rotor.
  • the oil may be supplied to compression tooth groove space of the male rotor in addition to the compression tooth groove space of the female rotor so as to perform a lubricating operation and a cooling operation. Further, since the primarily separated oil is supplied to the compression tooth groove space of the male rotor, it is possible to ensure the amount of the oil enough for keeping the sealing performance. As a result, it is possible to prevent the back flow of the gas between the tooth tip of the male rotor and the inner wall of the rotor chamber. Thus, the power necessary for driving the rotor in order to compress the leakage gas again may be decreased, and hence the amount of the air discharged from the compressor body may be also increased.
  • the secondary separation oil supply line may be connected to the primary separation oil supply line connected to the compression tooth groove space of the male rotor and may also supply the oil separated by the secondary separation unit to the compression tooth groove space of the male rotor.
  • the oil separated by the secondary separation unit may be supplied to the compression tooth groove space of the male rotor through the primary separation oil supply line.
  • the fluid mixture of the primarily separated oil and the secondarily separated oil including the compressed gas may be supplied to the compression tooth groove space of the male rotor in addition to the compression tooth groove space of the female rotor, the atomization of the oil is promoted when the fluid mixture is released to the compression tooth groove space of the male rotor. Accordingly, since the surface area of the oil with respect to the amount of the oil supplied to the male rotor increases, heat is easily exchanged between the oil supplied to the compressor body and the gas in the course of compression. Since the efficiency of the cooling process using the oil is improved, the gas almost becomes an isothermal compression state, and hence the power for driving the rotor decreases.
  • the compressor may further include a primary separation oil supply line that supplies oil to the bearing on the side of the discharge port, wherein the primary separation oil supply line that supplies oil to the discharge side bearing is provided with a throttle portion which decreases an oil supply amount.
  • the throttle portion Since the throttle portion is provided, the amount of the oil supplied to the bearing may be suppressed to the minimum amount necessary to lubricate the bearing. Meanwhile, even in the oil which increases in temperature after the lubrication of the bearing, there is no need to worry the suction even when the oil is returned to the suction space if the amount of the oil is extremely small. For that reason, since the throttle portion is provided, it is possible to select the suction space as a place where the oil lubricating the bearing while suppressing an increase in power necessary for a driving operation or degradation in performance may be returned.
  • FIG. 1A illustrates a compressor 1 according to a first embodiment of the present invention.
  • the compressor of the present invention is a screw type compressor 1, and is lubricated and cooled by oil flowing therein.
  • the compressor 1 includes a compressor body 10 and an oil collector 30.
  • the compressor body 10 includes a rotor casing 12 which is provided in a rotor chamber 11 therein so as to accommodate a screw rotor 20 to be described later in a rotatable state.
  • the compressor body 10 includes a suction port 13 which suctions a gas from the outside and a discharge port 14 which discharges a gas.
  • the screw rotor 20 includes a pair of rotors, that is, a female rotor 22 and a male rotor 24.
  • a tooth groove 27a is formed between a pair of teeth 22a and 22a adjacent to each other in the circumferential direction of the female rotor 22.
  • a compression tooth groove space 27 of the female rotor 22 is defined between the inner wall of the rotor chamber 11 as the inner surface of the rotor casing 12 and the pair of teeth 22a and 22a adjacent to each other in the circumferential direction of the female rotor 22.
  • a compression tooth groove space 28 of the male rotor 24 is defined between the inner wall of the rotor chamber 11 as the inner surface of the rotor casing 12 and a pair of teeth 24a and 24a adjacent to each other in the circumferential direction of the male rotor 24.
  • One of both rotors 22 and 24 is connected to an electric motor (not illustrated) provided in the rotor casing 12.
  • FIG. 1A representatively illustrates only the female rotor 22 as the screw rotor 20.
  • a gas which is suctioned from the upside through the suction port 13 in a manner such that an electric motor rotates the screw rotor 20 is compressed by the rotation of the female rotor 22 and the male rotor 24, and is discharged as a high-pressure gas to the downside through the discharge port 14.
  • the oil collector 30 includes a hollow cylinder 31, a separation unit 34 which serves as a primary separation unit including the inner wall (the inner wall surface) of the oil collector 30, a filter 32 which serves as a secondary separation unit, and an oil reservoir 33.
  • the discharged compression gas is introduced into the separation unit 34 of the oil collector 30 through a discharge line 35 including the discharge port 14 and the discharge passageway.
  • a compression air is introduced in a substantially tangential direction to an annular passageway formed between the hollow cylinder 31 and the inner wall of the oil collector 30, and the oil and the gas are centrifugally separated from each other by a swirl flow generated at that time. In this way, the oil is primarily separated from the compression gas which includes an oil element flowing into the oil collector 30 through the discharge line 35.
  • the compression gas from which the oil is primarily separated is guided to the filter 32 through the hollow cylinder 31.
  • the filter 32 is formed as, for example, a demister, and the oil is secondarily separated from the gas when the compression gas passes through the filter.
  • the oil reservoir 33 collects the oil which is primarily separated and falls along the inner wall surface of the oil collector 30 by the own weight.
  • the compression gas from which the oil is separated twice is supplied to a compression gas supply target through a supply pipe 36 communicating with the filter 32.
  • the compression gas is supplied to a gas supply target such as a factory.
  • the oil which is primarily separated from the gas inside the oil collector 30 is guided into the rotor casing 12 through a supply side line of an oil circulation line 40 causing the oil collector 30 and the compressor body 10 to communicate with each other.
  • the oil circulation line 40 includes a supply side line including a primary separation oil supply line 41, a secondary separation oil supply line 52, and a discharge side bearing oil drain line 54 and a collection side line including the discharge line 35.
  • One end of the primary separation oil supply line 41 communicates with the oil reservoir 33, and the other end thereof is divided into three sub-oil supply lines 42, 46, and 48.
  • the end of the rotor chamber oil supply line 42 as the sub-oil supply line 42 is divided into a female rotor side oil supply line 43 and a male rotor side oil supply line 44 (see FIG. 1B ).
  • the female rotor side oil supply line 43 communicates with the female rotor side compression tooth groove space 27 through an oil inflow port 17 which is provided in the rotor chamber 11 on the side of the female rotor 22.
  • the female rotor side oil supply line 43 is connected to the female rotor side compression tooth groove space 27 which is defined between the inner wall of the rotor chamber 11 and the pair of teeth 22a and 22a adjacent to each other in the female rotor 22 in the cross-section perpendicular to the rotor shaft of the compressor body 10 (see FIG. 1C ).
  • the oil inflow port 17 is provided at a position facing the female rotor 22 in the rotor chamber 11.
  • the male rotor side oil supply line 44 communicates with the male rotor side compression tooth groove space 28 through an oil inflow port 18 provided in the rotor chamber 11 on the side of the male rotor 24.
  • the male rotor side oil supply line 44 is connected to the male rotor side compression tooth groove space 28 which is defined between the inner wall of the rotor chamber 11 and the pair of teeth 24a and 24a adjacent to each other in the male rotor 24 in the cross-section perpendicular to the rotor shaft of the compressor body 10 (see FIG. 1C ).
  • the oil inflow port 18 is provided at a position facing the male rotor 24 in the rotor chamber 11.
  • the end of the discharge side bearing oil supply line 46 as the sub-oil supply line 46 communicates with the discharge side bearing 16.
  • the end of the suction side bearing oil supply line 48 as the sub-oil supply line 48 communicates with the suction side bearing 15.
  • a throttle portion 50 which reduces the oil supply amount to the discharge side bearing 16 is provided in the middle of the discharge side bearing oil supply line 46.
  • the throttle portion 50 is, for example, an orifice formed in an oil hole. Since the throttle portion 50 is provided, it is possible to suppress the amount of the oil necessary for lubricating the discharge side bearing 16 as minimal as possible.
  • the throttle portion 50 is provided in the middle of the suction side bearing oil supply line 48.
  • the discharge side bearing oil supply line 46 and the suction side bearing oil supply line 48 are provided with the throttle portion 50, but the present invention is not limited thereto.
  • a configuration may be employed in which the throttle portion 50 is provided only in the discharge side bearing oil supply line 46 in which the temperature of the oil used to lubricate the bearing easily increases.
  • One end of the secondary separation oil supply line 52 communicates with the filter 32 of the oil collector 30, and the other end thereof communicates with the female rotor side oil supply line 43 of the primary separation oil supply line 41 in a connection state. Furthermore, a fluid mixture obtained by mixing at least a part of the oil secondarily separated by the filter 32 and a part of the gas is guided into the secondary separation oil supply line 52.
  • One end of the discharge side bearing oil drain line 54 communicates with the discharge side bearing 16, and the other end thereof communicates with the inside of the rotor chamber 11 through a communication port 19 which is provided at a position just after the confinement of both rotors 22 and 24.
  • the oil which is primarily separated from the compression gas discharged from the compressor body 10 and is accumulated in the oil reservoir 33 is supplied to the compressor body 10 through the primary separation oil supply line 41.
  • the oil which is guided to the rotor chamber oil supply line 42 of the primary separation oil supply line 41 is supplied to the compression tooth groove space 27 of the female rotor 22 through the female rotor side oil supply line 43, and is supplied to the compression tooth groove space 28 of the male rotor 24 through the male rotor side oil supply line 44.
  • the oil which is supplied from the oil inflow ports 17 and 18 into the rotor chamber 11 is used to cool the compression gas, to lubricate the rotors 22 and 24, and to seal a gap between the rotors 22 and 24.
  • the oil which is secondarily separated by the filter 32 from the compression gas from which the oil is primarily separated is guided to the female rotor side oil supply line 43 through the secondary separation oil supply line 52. Accordingly, a fluid mixture of the primary separation oil and the pressurized gas including the secondary separation oil is injected toward the compression tooth groove space 27 of the female rotor 22 corresponding to the position in the course of the compression of the gas of the female rotor. Furthermore, when the pressure of the compression tooth groove space 27 of the female rotor 22 is too high, the oil supply amount decreases. For this reason, it is desirable to supply the fluid mixture to the compression tooth groove space 27 having a pressure less than an intermediate pressure between a suction pressure and a discharge pressure.
  • the secondary separation oil supply line 52 is connected to the female rotor side oil supply line 43 (the primary separation oil supply line 41), the fluid mixture of the oil and the gas is injected when the oil is supplied from the oil reservoir 33 to the compression tooth groove space 27 of the female rotor 22. For this reason, the dispersion of the oil released to the compression tooth groove space 27 is promoted and the deflection of the oil inside the tooth groove hardly occurs. Accordingly, oil shortage is prevented between the rotor chamber 11 and the tooth tip of the female rotor 22 as a portion in which partial oil shortage particularly easily occurs, and hence a back flow in which the gas in the course of compression leaks therebetween may be prevented. Thus, the power necessary for driving the rotors 22 and 24 in order to compress the leakage gas again decreases, and hence the amount of air discharged from the compressor body 10 may be also increased.
  • the fluid mixture of the oil and the pressurized gas is released to the compression tooth groove space 27 of the female rotor 22, the atomization of the oil is promoted, and hence the surface area of the oil with respect to the amount of the oil supplied to the female rotor 22 increases.
  • heat is easily exchanged between the fluid mixture supplied to the rotor chamber 11 and the gas in the course of compression. Accordingly, since the efficiency of the cooling process using the oil is improved, the gas almost becomes an isothermal compression state, and hence the power for driving the female rotor 22 decreases.
  • the tooth in the female rotor 22 generally has a narrow tooth tip width, and the amount of the gas leaking between the tooth tip of the female rotor 22 and the rotor chamber 11 easily affects the existence oil therebetween.
  • the merit in which the fluid mixture is supplied to the compression tooth groove space 27 of the female rotor 22 is larger than that of the case where the fluid mixture is supplied to the male rotor 24.
  • the present invention is not limited to the first embodiment, and may be modified into various forms.
  • the other end of the secondary separation oil supply line 52 is connected to only the female rotor side oil supply line 43, and communicates with the compression tooth groove space 27 of the female rotor 22 through the primary separation oil supply line 41.
  • the present invention is not limited thereto.
  • the other end of the secondary separation oil supply line 52 may be connected to the female rotor side oil supply line 43 and the male rotor side oil supply line 44, and may communicate with the compression tooth groove space 27 of the female rotor 22 and the compression tooth groove space 28 of the male rotor 24 through the rotor chamber oil supply line 42 as the primary separation oil supply line 41 (a second embodiment).
  • the fluid mixture of the primary separation oil and the gas including the secondary separation oil may be supplied to not only the female rotor 22, but also the compression tooth groove space 28 of the male rotor 24. Accordingly, since the fluid mixture is released to the compression tooth groove space 28 of the male rotor 24, the atomization of the oil is promoted, and hence the surface area of the oil with respect to the amount of the oil supplied to the male rotor 24 increases. Thus, heat is easily exchanged between the oil supplied to the compressor body 10 and the gas in the course of compression. Accordingly, since the efficiency of the cooling process using the oil is improved, the gas almost becomes an isothermal compression state, and hence the power for driving the rotors 22 and 24 may be decreased.
  • the dispersion of the oil when the fluid mixture is released to the compression tooth groove space 28 of the male rotor 24 is promoted, and hence the deflection of the oil inside a tooth groove 28a of the male rotor 24 hardly occurs. Accordingly, it is possible to improve the sealing performance inside the rotor chamber 11. Thus, the power necessary for driving the rotors 22 and 24 may be decreased, and the amount of air discharged from the compressor body 10 may be increased.
  • the other end of the secondary separation oil supply line 52 is connected to the female rotor side oil supply line 43 and the male rotor side oil supply line 44 through the rotor chamber oil supply line 42.
  • the secondary separation oil supply line 52 may be divided into the secondary separation oil supply line 52 connected to the female rotor side oil supply line 43 and the secondary separation oil supply line 52 connected to the male rotor side oil supply line 44.
  • the secondary separation oil supply line 52 may be a secondary separation oil supply line in which the line from one end to the other end thereof is separated or a secondary separation oil supply line in which one line is divided from the other end (see FIG. 4 ).
  • FIG. 3 illustrates a reference example in which the other end of the secondary separation oil supply line 52 is connected to only the male rotor side oil supply line 44 instead of the female rotor side oil supply line 43 (a reference example).
  • the specific power of the second embodiment is higher than that of the first embodiment.
  • energy may be saved in that the compressor of the first embodiment may compress a large amount of air by a power smaller than the compressor of the second embodiment.
  • the specific power is larger than those of the first embodiment and the second embodiment.
  • the compressors of the first embodiment and the second embodiment of the present invention including the primary separation oil supply line 41 which is connected to the oil collector 30 and the compression tooth groove space 27 of the female rotor 22 and supplies the oil separated by the separation unit 34 as the primary separation unit of the oil collector 30 to the compression tooth groove space 27 of the female rotor 22 and the secondary separation oil supply line 52 which supplies the oil separated by the filter 32 as the secondary separation unit to the compression tooth groove space 27 of the female rotor 22 and is connected to the primary separation oil supply line 41, it is proved that energy may be saved in that a large amount of air may be compressed by a power smaller than the compressor of the reference example.
  • the discharge side bearing oil supply line 46 and the suction side bearing oil supply line 48 are formed by dividing the primary separation oil supply line 41.
  • the present invention is not limited thereto, and the ends of the discharge side bearing oil supply line 46 and the suction side bearing oil supply line 48 may directly communicate with the oil reservoir 33.
  • a method of connecting the secondary separation oil supply line 52 to the primary separation oil supply line 41 is not limited to the above-described embodiment, and may be modified into various forms.
  • the end of the rotor chamber oil supply line 42 as the sub-oil supply line 42 is divided into the female rotor side oil supply line 43 and the male rotor side oil supply line 44.
  • the female rotor side oil supply line 43 and the male rotor side oil supply line 44 may be formed respectively as the separate primary separation oil supply lines.
  • the secondary separation oil supply line may be connected only to the female rotor side oil supply line 43.
  • the secondary separation oil supply line may be connected to the male rotor side oil supply line 44 in addition to the female rotor side oil supply line 43.
  • FIG. 6A illustrates the compressor 2 of a first comparative example in which the end of the secondary separation oil supply line 52 directly communicates with the rotor chamber 11.
  • the same reference numerals will be given to the same components as the compressor 1 of FIGS. 1A to 1C , and the repetitive description will not be presented.
  • the end of the rotor chamber oil supply line 42 communicates with the rotor chamber 11 through a primary separation oil inflow port 81 provided between the female rotor 22 and the male rotor 24 of the rotor chamber 11. That is, in the first comparative example, the end of the rotor chamber oil supply line 42 is connected to the compression tooth groove space as the connection portion of the compression tooth groove spaces 27 and 28 of the female and male rotors 22 and 24 defined by the inner wall of the rotor chamber 11 and the tooth 24a of the male rotor 24 and the tooth 22a of the female rotor 22 in the cross-section perpendicular to the rotor shaft of the compressor body 10.
  • the end of the secondary separation oil supply line 52 is located on the side of the suction side bearing 15 of the rotor chamber 11 in relation to the primary separation oil inflow port 81, and directly communicates with the rotor chamber 11 through a secondary separation oil inflow port 82 provided between the female rotor 22 and the male rotor 24.
  • the discharge side bearing oil drain line 54 communicates with the rotor chamber 11 through a communication port 83 provided between the female rotor 22 and the male rotor 24.
  • the communication port 83 is disposed between the primary separation oil inflow port 81 and the secondary separation oil inflow port 82 in the axial direction of the screw rotor 20.
  • the secondarily separated oil is directly returned to the low-pressure tooth grooves of the female rotor 22 and the male rotor 24 just after the compression start through the secondary separation oil inflow port 82 provided on the side of the suction side bearing 15 of the rotor chamber 11.
  • the temperature of a large amount of gas including the oil flowing through the secondary separation oil supply line 52 becomes higher than that of the gas in the low-pressure tooth groove.
  • FIGS. 7A and 7B illustrates the compressor 3 of a second comparative example in which the end of the discharge side bearing oil drain line 54 communicates with the rotor chamber oil supply line 42 in a connection state in addition to the end of the secondary separation oil supply line 52.
  • the same reference numerals will be given to the same components as the compressor 1 of FIGS. 1A to 1C , and the repetitive description will not be presented.
  • the rotor chamber oil supply line 42 communicates with the rotor chamber 11 through an oil inflow port 88 provided between the female rotor 22 and the male rotor 24 of the rotor chamber 11.
  • the end of the rotor chamber oil supply line 42 is connected to the compression tooth groove space as the connection portion of the compression tooth groove spaces 27 and 28 of the female and male rotors 22 and 24 defined by the inner wall of the rotor chamber 11 and the tooth 24a of the male rotor 24 and the tooth 22a of the female rotor 22 in the cross-section perpendicular to the rotor shaft of the compressor body 10.
  • the oil since the rotor chamber oil supply line 42 becomes a high pressure state, the oil is not easily returned from the discharge side bearing oil drain line 54 to the rotor chamber oil supply line 42, and the flow of the oil used to lubricate the discharge side bearing 16 is blocked. Accordingly, there is a concern that the lifetime of the discharge side bearing 16 may be degraded. Further, the mixing loss in the discharge side bearing 16 is large. In the second comparative example, the oil may not be forcedly caused to flow to the discharge side bearing 16 by using the existing oil line. For this operation, there is a need to provide an orifice and the like between the joint point of the secondary separation oil supply line 52 and the joint point of the discharge side bearing oil drain line 54 in the rotor chamber oil supply line 42.
  • the oil supply amount of the rotor chamber oil supply line 42 essentially decreases.
  • the oil supply amount to the rotor chamber 11 decreases, the compression gas temperature increases, and the leakage amount increases. Accordingly, there is a high possibility that the power necessary for driving the compressor increases and the amount of the discharge air decreases.
  • the second comparative example is not practical in that the power necessary for the driving operation may not be decreased, and is different from the first and second embodiments although there is similarity.
  • the first and second embodiments are practical in that the power necessary for driving the rotors 22 and 24 may be decreased and the amount of the air discharged from the compressor body 10 may be increased.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP14181227.1A 2013-10-15 2014-08-18 Screw Compressor and oil supply method thereof Active EP2863060B2 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2013214987A JP6126512B2 (ja) 2013-10-15 2013-10-15 圧縮機

Publications (3)

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EP2863060A1 EP2863060A1 (en) 2015-04-22
EP2863060B1 EP2863060B1 (en) 2016-07-13
EP2863060B2 true EP2863060B2 (en) 2019-03-20

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JP (1) JP6126512B2 (ja)
CN (1) CN104564686B (ja)
TW (1) TWI537471B (ja)

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JP6521781B2 (ja) * 2015-07-29 2019-05-29 株式会社神戸製鋼所 油冷式スクリュ圧縮機
BE1024462B1 (nl) * 2016-08-01 2018-03-05 Atlas Copco Airpower Naamloze Vennootschap Vloeistofgeïnjecteerd compressor- of expanderelement en werkwijze voor het regelen van de vloeistofinjectie van een compressor- of expanderinrichting
JP7072350B2 (ja) * 2017-05-24 2022-05-20 株式会社神戸製鋼所 油冷式圧縮機
JP6899288B2 (ja) 2017-09-04 2021-07-07 株式会社日立産機システム スクリュー圧縮機
CN111226040B (zh) * 2017-10-30 2020-11-03 株式会社爱发科 真空泵
US11965510B2 (en) * 2019-10-31 2024-04-23 Hitachi Industrial Equipment Systems Co., Ltd. Compressor body and compressor to supply liquid into working chambers and whose downstream portion reaches a suction bearing chamber

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DE102010002649A1 (de) † 2010-03-08 2011-09-08 Bitzer Kühlmaschinenbau Gmbh Schraubenverdichter
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DE1703251B2 (de) † 1967-05-03 1979-06-21 Svenska Rotor Maskiner Ab, Nacka (Schweden) Schraubenverdichter mit zwei Schraubenrotoren und ölzufuhr zum Arbeitsraum und zu Wellenlagern
JPS53118104A (en) † 1977-03-25 1978-10-16 Dainippon Ink & Chemicals Magnetic combination type recording material
DE2829338A1 (de) † 1977-07-05 1979-01-25 Compair Constr Mining Ltd Verfahren und kreiselverdichter zum abzug von oel aus einem getriebegehaeuse
JPS57135292A (en) † 1981-02-12 1982-08-20 Ebara Corp Screw compressor
US5037282A (en) † 1988-11-16 1991-08-06 Svenska Rotor Maskiner Ab Rotary screw compressor with oil drainage
JPH09303279A (ja) † 1996-05-14 1997-11-25 Hokuetsu Kogyo Co Ltd 油冷式スクリュ圧縮機
JP2001153073A (ja) † 1999-11-24 2001-06-05 Hitachi Ltd 給油式スクリュー圧縮機
JP2013214987A (ja) † 2002-02-13 2013-10-17 Interdigital Technology Corp トランスポートブロックセットのセグメント化
JP2005299467A (ja) † 2004-04-09 2005-10-27 Kobe Steel Ltd 油冷式圧縮機
JP2006214309A (ja) † 2005-02-02 2006-08-17 Hokuetsu Kogyo Co Ltd 油冷式スクリュ圧縮機の分離油回収構造
DE102010002649A1 (de) † 2010-03-08 2011-09-08 Bitzer Kühlmaschinenbau Gmbh Schraubenverdichter
JP2013036397A (ja) † 2011-08-09 2013-02-21 Hitachi Industrial Equipment Systems Co Ltd 給油式圧縮機

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EP2863060A1 (en) 2015-04-22
JP2015078623A (ja) 2015-04-23
CN104564686A (zh) 2015-04-29
JP6126512B2 (ja) 2017-05-10
CN104564686B (zh) 2017-01-18
TWI537471B (zh) 2016-06-11
TW201525290A (zh) 2015-07-01
EP2863060B1 (en) 2016-07-13

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