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WO2017014027A1 - Système à cycle de rankine - Google Patents

Système à cycle de rankine Download PDF

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Publication number
WO2017014027A1
WO2017014027A1 PCT/JP2016/069628 JP2016069628W WO2017014027A1 WO 2017014027 A1 WO2017014027 A1 WO 2017014027A1 JP 2016069628 W JP2016069628 W JP 2016069628W WO 2017014027 A1 WO2017014027 A1 WO 2017014027A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
working medium
receiver
circulation path
liquid pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2016/069628
Other languages
English (en)
Japanese (ja)
Inventor
智規 原口
和田　博文
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sanden Corp
Original Assignee
Sanden Holdings Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sanden Holdings Corp filed Critical Sanden Holdings Corp
Publication of WO2017014027A1 publication Critical patent/WO2017014027A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K27/00—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for
    • F01K27/02—Plants modified to use their waste heat, other than that of exhaust, e.g. engine-friction heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/14—Combined heat and power generation [CHP]

Definitions

  • the present invention relates to the configuration of the Rankine cycle system.
  • a waste heat power generation apparatus disclosed in Patent Document 1 includes a pump (liquid pump), an evaporator, a turbine generator (expander), a condenser, and a reservoir tank (receiver) in a circulation path of a working medium that is a fluid. It has a Rankine cycle system installed in order.
  • the working medium is pumped to the evaporator by a pump, and the working medium is evaporated by waste heat by the evaporator to form a gas.
  • the working medium that has become gas is rotated in the turbine generator while rotating the turbine to generate power, and is cooled in the condenser to become liquid.
  • the working medium cooled by the condenser is stored in a reservoir tank, and a liquid working medium is supplied to the pump.
  • the present invention has been made in view of such problems, and an object of the present invention is to provide a Rankine cycle system that suppresses gas mixing into a liquid pump and improves pump efficiency.
  • a Rankine cycle system of the present invention includes an evaporator that vaporizes a working medium by waste heat in a circulation path through which the working medium circulates, and an expansion that extracts energy by expanding the evaporated working medium.
  • a condenser that cools and liquefies the working medium that has passed through the expander, a receiver that gas-liquid separates the working medium that has passed through the condenser and discharges the liquid working medium, and the receiver
  • a Rankine cycle system including a liquid pump that pumps the working medium from the receiver toward the evaporator, wherein the liquid pump is disposed below the receiver, and the circulation path includes the receiver, the liquid pump, and the like. In the section between, it is inclined horizontally or downward from the receiver toward the liquid pump.
  • the ratio of the length of the horizontal portion in the circulation path in the section between the receiver and the liquid pump to the cross-sectional diameter of the circulation path is 10 or less.
  • the introduction path of the liquid pump for introducing the working medium from the circulation path to the pump chamber of the liquid pump is inclined downward from the circulation path toward the pump chamber.
  • the liquid pump includes a suction port portion connected to the circulation path via a connection joint, the main body portion of the liquid pump is disposed at an inclination, and the connection joint side of the suction port portion is It is good to incline upward from the horizontal.
  • the liquid pump includes a suction port connected to the circulation path via a connection joint, and the suction port is above the horizontal on the connection joint side with respect to the main body of the liquid pump. It is good to be inclined to.
  • a tapered portion that expands from the pump chamber side toward the receiver side is provided in a horizontal portion in the circulation path between the receiver and the pump chamber of the liquid pump.
  • the liquid pump is disposed below the receiver, and the circulation path is inclined horizontally or downward from the receiver toward the liquid pump in the entire section between the receiver and the liquid pump. Even if a part of the working medium that is liquid is vaporized in the section between the pump or the pump and the receiver, the gas in the working medium returns to the receiver. Thereby, it can suppress operating a pump in the state in which gas is mixed in the pump chamber, it can improve the startability of a pump, and can improve pump efficiency.
  • FIG. 1 is a schematic configuration diagram of a Rankine cycle system 1 according to an embodiment of the present invention.
  • the Rankine cycle system 1 is used, for example, in an apparatus that recovers waste heat from a factory or the like. As shown in FIG. 1, the Rankine cycle system 1 includes a pump 3 (liquid pump), an evaporator 4, an expander 5, a condenser 6, and a receiver tank 7 in order in a circulation path 2 through which a refrigerant (working medium) circulates. (Receiver).
  • a pump 3 liquid pump
  • evaporator 4 an expander 5
  • condenser 6 condenser 6
  • receiver tank 7 in order in a circulation path 2 through which a refrigerant (working medium) circulates. (Receiver).
  • the pump 3 is a liquid pump such as a gear pump.
  • the pump 3 may be a pump capable of pumping liquid, such as a vane pump, a diaphragm pump, or a piston pump, other than the gear pump.
  • the evaporator 4 is a heat exchanger that exchanges heat between waste heat such as exhaust heat and the refrigerant, and vaporizes the liquid refrigerant by the waste heat to be in a high-temperature and high-pressure superheated steam state.
  • the expander 5 expands the refrigerant in the superheated steam state generated by the evaporator, and converts the thermal energy of the refrigerant into torque (rotational force) and outputs it, for example, like a turbine.
  • the torque output from the expander 5 is transmitted to the generator 8 to drive the generator 8 and generate electric power.
  • the condenser 6 is a heat exchanger that exchanges heat between cooling water if water-cooled and air and refrigerant if air-cooled, and cools and liquefies the refrigerant.
  • the receiver tank 7 is a tank that stores the refrigerant cooled by the condenser 6.
  • the receiver tank 7 has a function of gas-liquid separation of a refrigerant in which gas and liquid are mixed and discharging only the liquid refrigerant to the pump 3.
  • the circulation path 2 is comprised by piping or a hose.
  • the pump 3 is arranged at the lowermost part of the circulation path 2.
  • the circulation path 2 in the section between the receiver tank 7 and the pump 3 is constituted by a pipe 10.
  • FIG. 2 is a diagram illustrating the shape of the pipe 10 between the receiver tank 7 and the pump 3 in the first embodiment. As shown in FIG. 2, in the first embodiment, the pipe 10 is inclined downward from the horizontal toward the pump 3 from the receiver tank 7 in the entire section between the receiver tank 7 and the pump 3. .
  • the pump 3 is arranged at the lowermost part of the circulation path 2, and the pipe 10 between the receiver tank 7 and the pump 3 is inclined downward from the horizontal in the entire section from the receiver tank 7 toward the pump 3.
  • the pipe 10 between the receiver tank 7 and the pump 3 is inclined downward from the horizontal in the entire section from the receiver tank 7 toward the pump 3.
  • FIG. 3 is a diagram illustrating the shape of the pipe 10 between the receiver tank 7 and the pump 3 in the second embodiment.
  • the pipe 10 between the receiver tank 7 and the pump 3 has a horizontal section 11 (horizontal portion) that extends horizontally at the connection portion with the pump 3. .
  • the piping 10 between the receiver tank and the pump is inclined downward from the horizontal toward the pump 3 from the receiver tank 7 side, as in the first embodiment, except for the horizontal section 11.
  • the ratio L / D between the length L and the inner diameter D (cross-sectional diameter) in the horizontal section 11 is set to a predetermined ratio a or less.
  • the predetermined ratio a may be set to 10 or less.
  • FIG. 4 is a graph showing the operating range of the pump 3 based on the ratio L / D between the length L and the inner diameter D and the degree of supercooling S in the horizontal section 11.
  • the degree of supercooling S is the amount of temperature decrease from the saturation temperature of the refrigerant temperature at the inlet of the pump 3.
  • the region where the degree of supercooling is larger than the line b shown in FIG. 4 is the normal operating region of the pump 3, and the region where the degree of supercooling is smaller than the line b is the malfunctioning region of the pump 3.
  • FIG. 5 is explanatory drawing which shows the state which the bubble collected in the horizontal area 11 in this embodiment.
  • the oblique line in FIG. 5 shows a liquid refrigerant.
  • the pump when the ratio L / D between the length L and the inner diameter D in the horizontal section 11 is equal to or greater than a predetermined ratio a, the pump is used even if the degree of supercooling S increases as the ratio L / D increases. It becomes easy to generate a malfunction. If the ratio L / D is equal to or less than the predetermined ratio a, the pump operates normally even if the degree of supercooling is 0 degree, that is, the refrigerant temperature at the inlet of the pump 3 is the same as the vaporization temperature of the refrigerant.
  • the predetermined ratio a is confirmed to be about 10 by the applicant's experiment.
  • the ratio L / D between the length L and the inner diameter D in the horizontal section 11 is suppressed to 10 or less, only a small amount of bubbles are accumulated in the horizontal section 11, for example, the horizontal section Even if the number of bubbles increases at 11, the bubbles overflow from the horizontal section 11 and return to the receiver tank 7 side in the pipe 10. Even if the pump 3 is started in a state where air bubbles are accumulated in the horizontal section 11, the thickness of the air bubble portion is smaller than the inner diameter D in the horizontal section 11 of the pipe 10. The amount of gas inflow relative to the amount of inflow of liquid refrigerant is suppressed, and malfunction of the pump 3 can be prevented.
  • FIG. 6 is the third embodiment
  • FIG. 7 is the fourth embodiment
  • FIG. 8 is the fifth embodiment
  • FIG. 9 is the shape of the pipe 10 between the receiver tank 7 and the pump 3 in the sixth embodiment.
  • the pipe 10 is connected to the pump 3 via a connecting joint 12 for piping.
  • the third embodiment shown in FIG. 6 differs from the second embodiment shown in FIG. 3 in that a connection joint 12 is provided in the horizontal section 11.
  • the mounting angle of the pump 3 is inclined, and the pipe 13 which is the suction port portion of the pump 3 is horizontally oriented from the main body portion 14 side of the pump 3 toward the connection joint 12 side. Also extends upwardly.
  • the pipe 13 and the straight connection joint 12 are connected to the pipe 10 that extends downwardly from the receiver tank 7.
  • the mounting angle of the pump 3 is not inclined, but the pipe 13 at the suction port of the pump 3 is inclined with respect to the main body 14 of the pump 3.
  • the main body 14 extends from the main body 14 toward the connection joint 12 while inclining upward from the horizontal.
  • the pipe 13 is connected to the pipe 10 extending obliquely downward from the receiver tank 7 through a straight connection joint 12.
  • connection joint 12 that connects the two uses a bent elbow joint.
  • the pipe 10 between the receiver tank 7 and the pump 3 is connected from the receiver tank 7 to the pump 3 as in the first embodiment. Since all the sections are inclined downward from the horizontal in all sections, it is possible to prevent bubbles from staying in the pipe 10 and to prevent the bubbles from being mixed into the pump 3, thereby improving the efficiency of the pump 3. Can be made.
  • the ratio L / D between the length L and the inner diameter D of the horizontal section 11 including the connection joint 12 may be set to 10 or less. Thereby, the efficiency of the pump 3 can be improved similarly to 2nd Embodiment.
  • FIG. 10 is a diagram illustrating the shape of the pipe 10 between the receiver tank 7 and the pump 3 in the seventh embodiment.
  • the inner diameter of the pipe 10 increases in a tapered shape from the tip connected to the connection joint 12 toward the receiver tank 7 side.
  • the taper portion 15 is different.
  • the tapered portion 15 by providing the tapered portion 15 in this manner, the upper portion of the inner wall surface of the pipe 10 in the horizontal section 11 is inclined upward from the connection joint 12 toward the receiver tank 7 side. become. Therefore, also in the seventh embodiment, bubbles are less likely to accumulate in the horizontal section 11, and the efficiency of the pump 3 can be improved.
  • FIG. 11 is an eighth embodiment
  • FIG. 12 is a ninth embodiment
  • FIG. 13 is a tenth embodiment
  • FIG. 14 is an internal configuration diagram of the pump 3 in the eleventh embodiment.
  • the eighth to eleventh embodiments are characterized by the shape of the suction port side in the pump 3.
  • the introduction path 22 for introducing the refrigerant into the pump chamber 21 in which the pair of rotating gears 20 is housed is upward from the pump chamber 21 toward the suction port 23 side. It is inclined to.
  • the suction port portion 24 connected to the pipe 10 is inclined upward.
  • the air is inclined downward in the pump 3 from the suction port 23 side, that is, the receiver tank 7 side toward the pump chamber 21. Is less likely to accumulate, and bubbles can be discharged to the receiver tank 7 side. Therefore, by adopting the eighth embodiment and the ninth embodiment as the configuration of the pump 3, it is difficult for bubbles to accumulate in the pump 3, and the efficiency of the pump 3 can be improved.
  • a tapered portion 25 is formed in which the inner diameter of the introduction path 22 is increased from the pump chamber 21 toward the suction port 23 side.
  • a tapered portion 25 is formed in which the inner diameter of the suction port portion 24 increases from the pump chamber 21 toward the suction port 23 side. Therefore, in the tenth embodiment and the eleventh embodiment, the upper portion of the inner wall surface of the tapered portion 25 extends from the pump chamber 21 to the suction port 23 in the pump 3 from the pump chamber 21 toward the suction port 23 side. It will incline upward between. As a result, even if the tenth embodiment and the eleventh embodiment are employed in the configuration of the pump 3, bubbles are less likely to accumulate in the pump 3, and the efficiency of the pump 3 can be improved.
  • the present invention is not limited to this form, and various modifications can be made without departing from the spirit of the present invention.
  • the receiver tank 7 and the pump 3 are connected by the pipe 10.
  • other pipes that can form a fluid flow path such as a hose may be used.
  • a plurality of the above embodiments 1 to 11 may be combined.
  • the Rankine cycle system 1 of the present embodiment is not limited to factory waste heat, and can be widely applied to Rankine cycles of various heat utilization devices.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

Le problème décrit par la présente invention est d'empêcher la contamination d'un gaz dans une pompe à liquide afin d'améliorer le rendement de la pompe. La solution selon la présente invention est un système à cycle de Rankine placé sur un trajet 2 de circulation à travers lequel circule un milieu de travail, doté : d'un évaporateur qui utilise la chaleur de déchets pour vaporiser le fluide de travail; d'un détendeur qui extrait l'énergie du milieu de travail en permettant au milieu de travail évaporé de se détendre; d'un condenseur qui refroidit et liquéfie le milieu de travail qui est passé à travers le détendeur; d'un réservoir (7) de réception qui soumet le milieu de travail qui est passé à travers le condenseur à une séparation vapeur-liquide et évacue le fluide de travail liquide; et d'une pompe (3) qui alimente le fluide de travail sous pression depuis le réservoir (7) de réception vers l'évaporateur. La pompe (3) est placée au-dessous du réservoir de réception (7), et un tuyau (10), qui est la partie du trajet (2) de circulation entre le réservoir (7) de réception et la pompe (3), est horizontal ou est incliné vers le bas depuis le réservoir (7) de réception vers la pompe (3), sur toute la longueur du tuyau (10).
PCT/JP2016/069628 2015-07-17 2016-07-01 Système à cycle de rankine Ceased WO2017014027A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015-142951 2015-07-17
JP2015142951A JP6615522B2 (ja) 2015-07-17 2015-07-17 ランキンサイクルシステム

Publications (1)

Publication Number Publication Date
WO2017014027A1 true WO2017014027A1 (fr) 2017-01-26

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PCT/JP2016/069628 Ceased WO2017014027A1 (fr) 2015-07-17 2016-07-01 Système à cycle de rankine

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JP (1) JP6615522B2 (fr)
WO (1) WO2017014027A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB169201A (en) * 1920-05-19 1921-09-19 Worthington Pump & Mach Corp Improvements in vacuum pumps particularly for use with condenser systems
JPS5369265A (en) * 1976-12-01 1978-06-20 Japan Steel Works Ltd Plastic melt extruder
JPS6324396U (fr) * 1986-07-31 1988-02-17
US6199382B1 (en) * 1998-11-25 2001-03-13 Penn State Research Foundation Dynamic condensate system
US20100192574A1 (en) * 2006-01-19 2010-08-05 Langson Richard K Power compounder
JP2013007367A (ja) * 2011-06-27 2013-01-10 Ihi Corp 廃熱発電装置及び発電装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB169201A (en) * 1920-05-19 1921-09-19 Worthington Pump & Mach Corp Improvements in vacuum pumps particularly for use with condenser systems
JPS5369265A (en) * 1976-12-01 1978-06-20 Japan Steel Works Ltd Plastic melt extruder
JPS6324396U (fr) * 1986-07-31 1988-02-17
US6199382B1 (en) * 1998-11-25 2001-03-13 Penn State Research Foundation Dynamic condensate system
US20100192574A1 (en) * 2006-01-19 2010-08-05 Langson Richard K Power compounder
JP2013007367A (ja) * 2011-06-27 2013-01-10 Ihi Corp 廃熱発電装置及び発電装置

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JP2017025737A (ja) 2017-02-02
JP6615522B2 (ja) 2019-12-04

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