US20170268498A1 - Multistage Compressor - Google Patents

Multistage Compressor Download PDF

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Publication number
US20170268498A1
US20170268498A1 US15/449,533 US201715449533A US2017268498A1 US 20170268498 A1 US20170268498 A1 US 20170268498A1 US 201715449533 A US201715449533 A US 201715449533A US 2017268498 A1 US2017268498 A1 US 2017268498A1
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Prior art keywords
valve
main body
compressor main
pressure
low
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Abandoned
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US15/449,533
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English (en)
Inventor
Masayuki Kasahara
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Hitachi Industrial Equipment Systems Co Ltd
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Hitachi Industrial Equipment Systems Co Ltd
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Assigned to HITACHI INDUSTRIAL EQUIPMENT SYSTEMS CO., LTD. reassignment HITACHI INDUSTRIAL EQUIPMENT SYSTEMS CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KASAHARA, MASAYUKI
Publication of US20170268498A1 publication Critical patent/US20170268498A1/en
Abandoned legal-status Critical Current

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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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F04C23/003—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle having complementary function
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/007—Installations or systems with two or more pumps or pump cylinders, wherein the flow-path through the stages can be changed, e.g. from series to parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B41/00—Pumping installations or systems specially adapted for elastic fluids
    • F04B41/06—Combinations of two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/08—Regulating by delivery pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2205/00—Fluid parameters
    • F04B2205/05—Pressure after the pump outlet

Definitions

  • the present invention relates to a multistage compressor and relates to a multistage compressor including a plurality of compressor main bodies.
  • a known gas compressor configured to suck gas (for example, air) to generate compressed gas (for example, compressed air) includes a multistage compressor that connects gas passages of a plurality of compressor bodies in series (hereinafter referred to as “multistage compressor”).
  • multistage compressors a gas discharge side of a low-pressure stage compressor main body and a gas suction side of a high-pressure stage compressor main body are connected through an inter cooler (intercooler), and gas is compressed in two-stages.
  • a two-stage compressor has a compression process close to isothermal compression as compared with the single stage compressor, so the compression efficiency can be increased and the temperature of each component such as a rotor and a casing becomes lower, and thus there is also little constraint on a heat resistance about materials and the like.
  • the speed of each stage is thus decided such that the compression ratio of a low-pressure stage compressor and the compression ratio of a high-pressure stage compressor become equal at a rated point.
  • the number of driving sources is one, and since transmitting power to a low-pressure stage compressor and a high-pressure stage compressor is performed by the gear having a constant speed increasing ratio with respect to each stage compressor, the speed ratio of a low-pressure stage compressor and a high-pressure stage compressor cannot be changed. Therefore, there is a case that the operation at the optimum speed ratio is not performed at the time of using the partial load.
  • JP 3352187 B2 discloses an operation method in which each of a low-pressure stage compressor main body and a high-pressure stage compressor main body is provided with a motor, which allows an independent drive, the intermediate pressure is detected, and the rotational speed is adjusted based on the detection pressure. For example, when the amount of air used decreases and the rotation speed decreases, the intermediate pressure becomes high.
  • a control signal is outputted to an inverter from a controller so as to decrease the rotational speed of a low-pressure stage compressor main body or increase the rotational speed of a high-pressure stage compressor main body.
  • the compression ratio of each stage can be made equal at the time of partial load also, and efficient operation will be achieved.
  • JP 3352187 B2 requires two motors, which are main parts of the compressor system. In addition, when increasing the speed by gears or belts, the number of these parts also increases. Thus, independent control of the rotational speed of each stage only for optimization of intermediate pressure increases the number of parts, and various problems such as the increase in material cost, required space, and also maintenance cost remain.
  • compressors for high pressure and low pressure may be provided separately, but there are problems of increase in installation area or mounting area and increase in cost.
  • one compressor can allow the selective use of both compressors.
  • high-pressure compressed gas is generated from a compressor, and this gas is stored in a reservoir tank, and when a low-pressure compressed gas is required, the pressure is reduced to a desired pressure before use. Reduced pressure in this manner results in loss of the high-pressure compressed gas energy.
  • the configuration is a multistage compressor including: at least a first compressor main body 1 and a second compressor main body 2 configured to suck compressed gas discharged from the first compressor main body 1 to discharge the compressed gas with higher pressure; a first driving source 3 configured to drive the first compressor main body 1 ; a second driving source 4 configured to drive the second compressor main body 2 ; an intermediate pipe configured to connect a discharge side of the first compressor main body 1 and a suction side of the second compressor main body 2 ; a low-pressure side discharge piping system branched from the intermediate pipe; an on-off valve 13 disposed in the low-pressure side discharge piping system and configured to switch permission and prohibition of a flow of compressed gas discharged from the first compressor main body 1 ; and a control unit 10 configured to control driving of the first driving source 3 and the second driving source 4 , wherein the control unit 10 is configured to drive the first driving source 3 alone when the on-off valve 13 is opened.
  • another configuration is a multistage compressor including: at least a first compressor main body 1 and a second compressor main body 2 configured to suck compressed gas discharged from the first compressor main body 1 to discharge the compressed gas with higher pressure; a first driving source 3 configured to drive the first compressor main body 1 ; a second driving source 4 configured to drive the second compressor main body 2 ; an intermediate pipe which connects a discharge side of the first compressor main body 1 , and a suction side of the second compressor main body 2 ; a low-pressure side discharge piping system branched from the intermediate pipe; an on-off valve 13 disposed in the low-pressure side discharge piping system and configured to switch permission and prohibition of a flow of compressed gas discharged from the first compressor main body 1 ; a by-pass pipe 25 configured to a discharge pipe of the second compressor main body 2 and a downstream side of the on-off valve 13 of the low-pressure side discharge pipe; a by-pass valve 26 configured to switch permission and prohibition of a flow of compressed gas into the by-pass pipe 25
  • FIG. 1 is a block diagram schematically showing a configuration of an oilless screw compressor according to Embodiment 1 to which the present invention is applied;
  • FIG. 2 is a cross-sectional view showing a compressor body configuration of an oilless screw compressor in detail, and a schematic view of its control system diagram according to Embodiment 1;
  • FIG. 3 is a block diagram schematically showing a configuration of an oilless screw compressor according to Embodiment 2 to which the present invention is applied.
  • FIG. 4 is a block diagram schematically showing a configuration of an oilless screw compressor according to Embodiment 3 to which the present invention is applied.
  • FIG. 1 is a schematic view of a two-stage screw air compressor (hereinafter simply referred to as “compressor”) 20 A, and a configuration of a compressor system (including a high-pressure/low-pressure air lines, a reservoir tank 8 and the like), and a gas flow according to Embodiment 1 to which the present invention is applied.
  • a compressor system including a high-pressure/low-pressure air lines, a reservoir tank 8 and the like
  • a gas flow according to Embodiment 1 to which the present invention is applied.
  • an oilless screw air compressor is applied in this embodiment, the present invention is not limited thereto, and a liquid supply (oil, water, etc.) type compressor may be applied.
  • Compression mechanism such as scroll, reciprocation, vane or the like may be applied, and multistage configurations from a combination of various types and the like may be applied.
  • Various configurations are applicable within a scope not deviating from the spirit thereof.
  • the compressor 20 A includes a low-pressure stage compressor main body 1 , a driving source (for example, motor 3 ) configured to drive the low-pressure stage compressor main body 1 , a high-pressure stage compressor main body 2 , a driving source (motor 4 ) that is configured to drive the high-pressure stage compressor main body 2 , an intercooler 6 , and aftercooler 7 .
  • a piping system of the discharge side of the low-pressure stage compressor main body 1 is connected with a piping system of the suction side of the high-pressure stage compressor main body 2 in series.
  • the low-pressure stage compressor main body 1 compresses the suction atmosphere from the outside, and the discharged compressed air is intercooled by the intercooler 6 .
  • the high-pressure stage compressor main body 2 sucks this cooled air, and further pressurizes it, discharges more high-pressure compressed air, and the resultant compressed air is cooled by the aftercooler 7 to a predetermined temperature.
  • the intermediate piping system connected to the high-pressure stage compressor main body 2 from the intercooler 6 branches from its midway.
  • One branch pipe is provided with a low-pressure stage discharge check valve 19 and a low-pressure line discharge valve (on-off valve) 13 , and is connected to one or more low-pressure air lines 100 to supply low-pressure compressed air to customers.
  • the low-pressure line discharge valve 13 and the low-pressure stage discharge check valve 19 permit or prohibit flow in the low-pressure air line 100 from an intermediate pipe.
  • the other branch pipe is connected to the suction side of the high-pressure stage compressor main body 2 through a high-pressure stage suction valve 14 .
  • the discharge side piping system of the high-pressure stage compressor main body 2 is provided with a high-pressure stage discharge check valve 18 and the aftercooler 7 where the high-pressure stage discharge check valve 18 is disposed upstream of the aftercooler 7 , and the discharge side piping system is connected with the reservoir tank 8 disposed outside of the compressor 20 A.
  • the reservoir tank 8 is connected with one or more high-pressure air lines 200 to supply high-pressure compressed air to customers.
  • the compressor 20 A includes a pressure sensor 21 that detects the discharge pressure of the low-pressure stage compressor main body 1 and which is disposed between the downstream side of the intercooler 6 and the branch point of the intermediate pipe.
  • the reservoir tank 8 is provided with a pressure sensor 22 which detects the internal pressure of the reservoir tank 8 .
  • the pressure sensor 22 may be disposed in a piping system downstream from the high-pressure stage discharge check valve 18 in the compressor 20 A.
  • the detection pressure of each pressure sensor 21 and 22 is inputted into a control unit 10 which is communicably connected with each pressure sensor 21 and 22 , and the control unit 10 controls the drive rotation of the motors 3 and 4 according to these pressure values.
  • inverters 11 A and 11 B are provided for the motors 3 and 4 , respectively, and the control unit 10 performs variable speed control through the inverters.
  • FIG. 2 shows a specific configuration of each of compressor main bodies, motors and the like on the low-pressure stage side and the high-pressure stage side.
  • the low-pressure stage compressor main body 1 includes a pair of male and female screw rotors 51 a and 51 b in a compression chamber formed in a compressor main body casing 50 .
  • the respective screw rotors mesh with each other in a non-contact manner through a predetermined gap, and the rotors and the inner wall of the compression chamber serve as a compression operating chamber.
  • the shaft of the male rotor is formed in series with a main shaft 52 of the motor 3 in the coaxial direction, and a timing gear 53 which meshes with the gear installed at the end portion of the female rotor to transmit power is disposed at the opposite side end portion of the motor 3 in the axial direction.
  • the compressor main body casing 50 and a motor casing 55 are integrally connected along the shaft.
  • the rotor 51 a and a main shaft 52 of the motor are directly connected in this embodiment, gear connection or belt drive may be applied.
  • the motor 3 and the like are a radial motor as an example, other types of motors such as an axial motor and the like may be used.
  • the high-pressure stage compressor main body 2 has substantially similar configuration as the low-pressure stage compressor main body 1 except that the high-pressure stage compressor main body 1 has a smaller compression volume and a higher number of revolutions.
  • each compressor main body receives power supply from the inverters 11 a and 11 b, respectively.
  • Each of the inverters 11 a and 11 b is configured so that the control unit 10 can independently transmit rotational frequency command values. Accordingly, the low-pressure stage compressor main body 1 and the high-pressure stage compressor main body 2 can be independently controlled.
  • the rotational drive ratio of each compressor body is fixed, and it is impossible to perform drive control of either one alone.
  • the compressor 20 A of the present embodiment is characterized in that the drive control of either one alone is possible.
  • the control unit 10 is a function part in which cooperation of an arithmetic unit and a program is performed. It has an external input/output interface (not shown), receives various inputs relating to setting values, switching of operation modes and the like, and can appropriately outputs driving conditions and various control information.
  • the control unit 10 is communicatively connected with the pressure sensors 21 and 22 (dot-and-dash line in the figure), and performs control according to the detection pressure. Further, it is connected to a solenoid valve such as a low-pressure line discharge valve 13 and a high-pressure stage suction valve 14 (dotted line in the figure) to control opening and closing operations of these valves.
  • a solenoid valve such as a low-pressure line discharge valve 13 and a high-pressure stage suction valve 14 (dotted line in the figure) to control opening and closing operations of these valves.
  • One feature of the compressor 20 A having such a configuration is that it can use separately both of low-pressure compressed air generated by the low-pressure stage compressor main body 1 alone, and high-pressure compressed air generated from the low-pressure stage compressor main body 1 and the high-pressure stage compressor main body 2 to supply each air to customers. Specifically, (1) when using low-pressure compressed air generated by the low-pressure stage compressor main body 1 alone, the low-pressure line discharge valve 13 is “opened”, the high-pressure stage suction valve 14 is “closed”, and the operation of the high-pressure stage compressor main body 2 is stopped.
  • both of the low-pressure line discharge valve 13 and the high-pressure stage suction valve 14 are “opened”, and both of low-pressure stage compressor main bodies 1 and high-pressure stage compressor main bodies 2 are operated.
  • the low-pressure line discharge valve 13 is “opened”, the high-pressure stage suction valve 14 is “closed”, and operation of the high-pressure stage compressor main body 2 stops. Accordingly, high-pressure stage compressor main body 2 is separated from the operation system, and the compressed air can be supplied only to the low-pressure air line 100 .
  • the ratio (n 1 /n 2 ) of speed n 1 of the low-pressure stage compressor main body 1 to speed n 2 of the high-pressure stage compressor main body 2 is increased relative to the rating so as to raise the intermediate pressure.
  • the control unit 10 determines a rotational speed ratio so that the compression ratio in the low-pressure stage compressor main body 1 and the compression ratio in the high-pressure stage compressor main body 2 are made to be equal.
  • the compressor 20 A can achieve three kinds of air supply modes, which are a supply of compressed air generated by driving the low-pressure stage compressor main body 1 alone, a supply of compressed air generated by driving the two-stage compressor main bodies 1 and 2 , which is an ordinal supply, and a supply of compressed air generated by driving the two-stage compressor main bodies 1 and 2 , and compressed air generated by driving the low-pressure stage compressor main body 1 alone.
  • one two-stage compressor has a configuration such that it can be used as a single stage compressor, a two-stage compressor, and a single-stage/two-stage simultaneously driven compressor, and achieves users' advantage relating to installation location and cost aspect, and also manufacturers' merits such as a reduction in the number of parts.
  • a compressor 20 B according to Embodiment 2 of the present invention will be described.
  • the main difference from Embodiment 1 is that the high-pressure stage suction valve 14 of Embodiment 1 is not provided and a by-pass pipe 25 is connected between a pipe between the low-pressure stage discharge check valve 19 in the low-pressure air line 100 side piping system and the low-pressure line discharge valve 13 , and a pipe from the discharge side of the high-pressure stage compressor main body 1 , a discharge side by-pass valve 26 is provided midway of this by-pass pipe 25 , and in addition, in the discharge side pipe of the high-pressure stage compressor main body 2 , a pressure regulating check valve 27 is provided downstream of the branch point with the by-pass pipe 25 .
  • the compressor 20 B of Embodiment 2 is capable of supplying the compressed air generated by the low-pressure stage compressor main body 1 alone to the low-pressure air line and can perform the normal operation of the two-stage compressor. It does not operate to supply compressed air to both the high-pressure air line and the low-pressure air line by driving both compressor main bodies.
  • the other configuration is similar to that of Embodiment 1.
  • the same reference numerals are used for the same members and elements. Detailed description will be omitted.
  • Embodiment 1 invites a slight pressure loss of the compressed air which passes through it, in cases of the configuration of Embodiment 2, there is the advantage that such pressure loss does not occur at the time of the normal operation of the two-stage compressor.
  • the pressure regulating check valve 27 is a check valve which restricts flow of compressed air when the pressure is lower than a predetermined pressure.
  • the pressure regulating check valve 27 in the pressure environment in which only the low-pressure stage compressor main body 1 is driven, the pressure regulating check valve 27 serves as “closed”, and it serves as “opened” in the high-pressure discharge environment during the normal operation of the two-stage compressor.
  • the discharge side by-pass valve 26 is an electromagnetic valve, and is controlled by the control unit 10 .
  • the discharge side by-pass valve 26 drives the low-pressure stage compressor main body 1 alone, and in cases where it supplies compressed air to the low-pressure air line, it serves as “opened”, and serves as “close” at the time of the normal operation of the two-stage compressor.
  • a compressor 20 C according to Embodiment 3 of the present invention will be described.
  • the main differences between Embodiment 3 and other embodiments is that when compressed air is supplied to the low-pressure air line alone, either one of the low-pressure stage compressor main body 1 or the high-pressure stage compressor main body 2 is selectively operated so that compressed air can be supplied.
  • compressor air When compressor air is supplied only to the low-pressure air line, in cases where the amount of air used is small, it is generally more efficient to operate the high-pressure stage compressor with a smaller volume at a higher speed than operating the low-pressure stage compressor at a low speed.
  • FIG. 4 shows a schematic configuration of the compressor 20 C according to Embodiment 3.
  • the same reference numerals are used for the same members and elements, and a detailed description will be omitted.
  • the suction side piping system of the low-pressure stage compressor main body 1 branches.
  • One pipe serves as a suction system of the low-pressure stage compressor main body 1
  • another pipe 40 serves as a suction pipe connected so that it may communicate with the intermediate pipe.
  • the pipe 40 may be connected to the suction side of the high-pressure stage compressor main body 2 without being connected to the intermediate pipe.
  • the pipe 40 is provided with a solenoid valve (valve body) 36 , and the opening and closing of the pipe 40 is controlled by the control unit 10 so that the flow of gas in the pipe 40 is permitted or prohibited.
  • Embodiment 3 has a by-pass pipe 25 branched from the discharge side piping system of the high-pressure stage compressor main body 2 to extend to the low-pressure air line 100 .
  • This embodiment has a configuration such that the by-pass pipe 25 branches from the outlet or the middle of aftercooler 7 to extend to the low-pressure air line 100 .
  • the compressor 20 C having the above configuration, when supplying the compressed air only to the low-pressure air line, in cases where the amount of air is large, the low-pressure stage compressor main body 1 alone is operated whit the low-pressure line discharge valve 13 “opened”, and the electromagnetic valve 36 and the by-pass valve 26 “opened”. On the other hand, when the amount of air is small, in the compressor 20 , the high-pressure stage compressor main body 2 alone is operated with the low-pressure line discharge valve 13 , the electromagnetic valve 36 and the by-pass valve 26 “closed”.
  • the high-pressure stage compressor main body 2 sucks the outside air which does not pass through the discharge port of the low-pressure stage compressor main body 1 , and generates the compressor air supplied to the low-pressure air line 100 .
  • the compressor 20 C makes all the low-pressure line discharge valve 13 , the electromagnetic valve 36 , and the by-pass valve 26 “closed”. Further, when air is supplied to both air lines, the low-pressure line discharge valve 13 is “opened”, the electromagnetic valve 36 and the by-pass valve 26 are “closed”, and operation is performed by changing the operation speed ratio of the low-pressure stage compressor main body 1 and the high-pressure stage compressor main body 2 according to the amount of used air.
  • the compressor 20 C of Embodiment 3 when compressed air is supplied to the low-pressure air line alone, either the low-pressure stage compressor main body 1 or the high-pressure stage compressor main body 2 is selected according to the amount of compressed air to supply, and the compressed air can be supplied more efficiently.
  • the present invention is not limited to the above-described various configurations and the like, and various modifications are possible without departing from the spirit thereof. It is also possible to replace the configuration of a specific embodiment with other embodiments.
  • the low-pressure line discharge valve 13 and the like are controlled by the control unit 10 , but instead, a part or the whole of the electromagnetic valve may be a manual valve body, the operation may be such that compressed air is supplied to the low-pressure air line by the switching operation by the user.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
US15/449,533 2016-03-16 2017-03-03 Multistage Compressor Abandoned US20170268498A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016-051854 2016-03-16
JP2016051854A JP6670645B2 (ja) 2016-03-16 2016-03-16 多段圧縮機

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TWI663334B (zh) * 2018-01-04 2019-06-21 大陸商復盛實業（上海）有限公司 級間泄放式空氣壓縮機
WO2019143835A1 (en) * 2018-01-18 2019-07-25 Maynard Mark J Gaseous fluid compression with alternating refrigeration and mechanical compression
KR20190138742A (ko) * 2018-06-06 2019-12-16 가부시키가이샤 고베 세이코쇼 압축 장치
US10563621B2 (en) * 2016-01-18 2020-02-18 Cryostar Sas System for supplying compressed gas to several gas-fed devices
WO2020065504A1 (en) * 2018-09-25 2020-04-02 Atlas Copco Airpower, Naamloze Vennootschap Oil-injected multi-stage compressor system and procedure for controlling such a compressor system
WO2020065506A1 (en) * 2018-09-25 2020-04-02 Atlas Copco Airpower, Naamloze Vennootschap Oil-injected multistage compressor device and method for controlling a compressor device
BE1026654B1 (nl) * 2018-09-25 2020-04-27 Atlas Copco Airpower Nv Oliegeïnjecteerde meertraps compressorinrichting en werkwijze voor het aansturen van een compressorinrichting
US11067075B2 (en) * 2017-05-05 2021-07-20 Zf Cv Systems Europe Bv Method for operating a pressure control system comprising a multi-stage compressor, and pressure control system
US11773853B2 (en) 2019-02-06 2023-10-03 Hitachi Industrial Equipment Systems Co., Ltd. Multi-stage screw compressor
US12049899B2 (en) 2017-08-28 2024-07-30 Mark J. Maynard Systems and methods for improving the performance of air-driven generators using solar thermal heating

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107939720A (zh) * 2018-01-12 2018-04-20 新余钢铁集团有限公司 一种多级压缩机设备出口输出压力切换结构
CN108757422A (zh) * 2018-05-07 2018-11-06 杰瑞石油天然气工程有限公司 一种多级压缩机组排量调节方法
WO2020195532A1 (ja) * 2019-03-27 2020-10-01 株式会社日立産機システム 圧縮機
CN110319008A (zh) * 2019-08-08 2019-10-11 珠海格力电器股份有限公司 具有两级排气功能的压缩机及空调系统

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120260693A1 (en) * 2011-04-15 2012-10-18 Demore Daniel D Compression method and air separation
US9879827B2 (en) * 2015-03-18 2018-01-30 Hanwha Techwin Co., Ltd. Compressor system

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61149597A (ja) * 1984-12-21 1986-07-08 Hitachi Ltd 多段圧縮機の運転制御装置
JPS6387556A (ja) * 1986-09-30 1988-04-18 株式会社東芝 ヒ−トポンプ装置
JPH0544678A (ja) * 1991-08-13 1993-02-23 Matsushita Electric Ind Co Ltd 密閉型ロータリー圧縮機
JP3352187B2 (ja) * 1993-12-03 2002-12-03 株式会社神戸製鋼所 ２段型オイルフリースクリュ圧縮機
JP2003129961A (ja) * 2001-10-25 2003-05-08 Hitachi Ltd 燃料電池用圧縮機
JP2005240787A (ja) * 2004-03-01 2005-09-08 Hitachi Industrial Equipment Systems Co Ltd パッケージ型圧縮機
JP5071967B2 (ja) * 2007-03-30 2012-11-14 アネスト岩田株式会社 ロータリコンプレッサ及びその運転制御方法
JP5341075B2 (ja) * 2008-05-23 2013-11-13 パナソニック株式会社 流体機械および冷凍サイクル装置
US20120263605A1 (en) * 2011-04-15 2012-10-18 Demore Daniel D Compression method and air separation
JP5714479B2 (ja) * 2011-12-26 2015-05-07 株式会社神戸製鋼所 油冷式２段圧縮機及びヒートポンプ
JP6276120B2 (ja) * 2014-06-27 2018-02-07 株式会社神戸製鋼所 ガス圧縮装置
CN105241125B (zh) * 2015-11-06 2018-01-16 珠海格力节能环保制冷技术研究中心有限公司 压缩机、制冷系统以及压缩机降温增气的方法

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120260693A1 (en) * 2011-04-15 2012-10-18 Demore Daniel D Compression method and air separation
US9879827B2 (en) * 2015-03-18 2018-01-30 Hanwha Techwin Co., Ltd. Compressor system

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10563621B2 (en) * 2016-01-18 2020-02-18 Cryostar Sas System for supplying compressed gas to several gas-fed devices
US11067075B2 (en) * 2017-05-05 2021-07-20 Zf Cv Systems Europe Bv Method for operating a pressure control system comprising a multi-stage compressor, and pressure control system
US12049899B2 (en) 2017-08-28 2024-07-30 Mark J. Maynard Systems and methods for improving the performance of air-driven generators using solar thermal heating
TWI663334B (zh) * 2018-01-04 2019-06-21 大陸商復盛實業（上海）有限公司 級間泄放式空氣壓縮機
US10989110B2 (en) 2018-01-18 2021-04-27 Mark J. Maynard Gaseous fluid compression with alternating refrigeration and mechanical compression using a first and second bank of compression coupled with first and second cascading heat pump intercoolers having a higher and a lower temperature section
WO2019143835A1 (en) * 2018-01-18 2019-07-25 Maynard Mark J Gaseous fluid compression with alternating refrigeration and mechanical compression
KR102302946B1 (ko) * 2018-06-06 2021-09-17 가부시키가이샤 고베 세이코쇼 압축 장치
US11085429B2 (en) * 2018-06-06 2021-08-10 Kobe Steel, Ltd. Compression device
KR20190138742A (ko) * 2018-06-06 2019-12-16 가부시키가이샤 고베 세이코쇼 압축 장치
BE1026654B1 (nl) * 2018-09-25 2020-04-27 Atlas Copco Airpower Nv Oliegeïnjecteerde meertraps compressorinrichting en werkwijze voor het aansturen van een compressorinrichting
BE1026651B1 (nl) * 2018-09-25 2020-04-28 Atlas Copco Airpower Nv Oliegeïnjecteerde meertraps compressorinrichting en werkwijze om een dergelijke compressorinrichting aan te sturen
WO2020065506A1 (en) * 2018-09-25 2020-04-02 Atlas Copco Airpower, Naamloze Vennootschap Oil-injected multistage compressor device and method for controlling a compressor device
WO2020065504A1 (en) * 2018-09-25 2020-04-02 Atlas Copco Airpower, Naamloze Vennootschap Oil-injected multi-stage compressor system and procedure for controlling such a compressor system
US11519412B2 (en) 2018-09-25 2022-12-06 Atlas Copco Airpower. Naamloze Vennootschap Oil-injected multistage compressor device and method for controlling a compressor device
US12018678B2 (en) 2018-09-25 2024-06-25 Atlas Copco Airpower, Naamloze Vennootschap Oil-injected multi-stage compressor system and procedure for controlling such a compressor system
CN109469598A (zh) * 2019-01-21 2019-03-15 贵州电网有限责任公司 一种压缩空气储能压气机系统及其控制方法
US11773853B2 (en) 2019-02-06 2023-10-03 Hitachi Industrial Equipment Systems Co., Ltd. Multi-stage screw compressor

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