WO2011128284A1 - Passage tournant pour vapeur surchauffée - Google Patents

Passage tournant pour vapeur surchauffée Download PDF

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Publication number
WO2011128284A1
WO2011128284A1 PCT/EP2011/055598 EP2011055598W WO2011128284A1 WO 2011128284 A1 WO2011128284 A1 WO 2011128284A1 EP 2011055598 W EP2011055598 W EP 2011055598W WO 2011128284 A1 WO2011128284 A1 WO 2011128284A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft
sealing
rotary feedthrough
distribution chamber
pressure distribution
Prior art date
Application number
PCT/EP2011/055598
Other languages
German (de)
English (en)
Inventor
Uwe Kark
Original Assignee
Kark Ag
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 Kark Ag filed Critical Kark Ag
Publication of WO2011128284A1 publication Critical patent/WO2011128284A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L27/00—Adjustable joints, Joints allowing movement
    • F16L27/08—Adjustable joints, Joints allowing movement allowing adjustment or movement only about the axis of one pipe
    • F16L27/087—Joints with radial fluid passages
    • F16L27/093—Joints with radial fluid passages of the "banjo" type, i.e. pivoting right-angle couplings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S30/00—Arrangements for moving or orienting solar heat collector modules
    • F24S30/40—Arrangements for moving or orienting solar heat collector modules for rotary movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S80/00—Details, accessories or component parts of solar heat collectors not provided for in groups F24S10/00-F24S70/00
    • F24S80/30—Arrangements for connecting the fluid circuits of solar collectors with each other or with other components, e.g. pipe connections; Fluid distributing means, e.g. headers
    • 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
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/40—Solar thermal energy, e.g. solar towers
    • Y02E10/47—Mountings or tracking

Definitions

  • the invention relates to a rotary feedthrough for superheated steam, in particular for use in solar thermal systems.
  • the invention further relates to a system of a solar thermal system, comprising a solar thermal collector and a rotary feedthrough.
  • the incident solar radiation is focused by means of an optical element, for example a Fresnel lens, onto an absorber through which heat transfer fluid flows.
  • an optical element for example a Fresnel lens
  • the energy stored in the form of heat in the heat transfer fluid can then be fed via pipelines connected to the solar collector devices, eg. Heat exchangers, and made usable there.
  • the heat transfer fluid in the absorber is heated so much that it participates in a phase transition towards the gaseous form.
  • the gaseous heat transfer fluid can then be used to drive a turbine, where it cools again, goes into a liquid state and the absorber can be fed again.
  • the optical element should always perpendicular to the be aligned with incident solar radiation. It is known to mount the solar collector for this purpose pivotable about at least one axis, so that the optical element can be tracked to the position of the sun.
  • the absorber usually firmly connected to the optical element. Therefore, the position of the absorber changes in the above-described tracking of the solar collector. Depending on whether a one- or two-axis tracking of the solar collector takes place, the absorber is pivoted about one or two axes. Nevertheless, the supply and discharge of heat transfer fluid - and thus the flow through the absorber - must be ensured.
  • the invention has for its object to provide a device which allows the supply and discharge of heat transfer fluid in the liquid or gaseous state along a pivot axis of a solar thermal collector.
  • the invention relates to a rotary feedthrough for heat transfer fluid in the liquid or gaseous state for use in solar thermal systems
  • a shaft with a hollow bore, a pressure-distribution space annularly surrounding the shaft, which is bounded in the axial direction by at least one spring collar fixedly connected to the shaft, and with a arranged in the region of the pressure distribution chamber connecting bore through the wall of the Hollow bore, as well as at least one sealing and bearing bush, wherein each of the sealing and bearing bushes is flush against the side facing away from the pressure distribution chamber side of their respective adjacent spring collar and biased against it.
  • the invention further relates to a system comprising a thermal solar collector mounted pivotably about at least one pivot axis with an optical element and an absorber, which is designed to flow through with heat transfer fluid, and at least one rotary union with a shaft having a hollow bore, a pressure distribution chamber surrounding the shaft which is bounded in the axial direction by at least one spring collar fixedly connected to the shaft, and with a connection bore arranged in the region of the pressure distribution chamber through the wall of the hollow bore, and at least one sealing and bearing bush, each sealing and bearing bush being flush the side facing away from the pressure distribution chamber side of the respective adjacent Federbundes and biased against it, wherein the shaft of the at least one rotary feedthrough is arranged coaxially with one of the at least one pivot axis and the absorber of the thermal solar collector rotates firmly and fluidly connected to the hollow bore or the pressure distribution chamber.
  • heat transfer fluid can be introduced into the pressure distribution chamber.
  • the pressure distribution chamber is arranged in a ring around the shaft and limited by at least one, with the shaft fixed and pressure-tight connected spring collar. It is preferred if the pressure chamber is delimited by two (spaced apart) spring collars, so that the pressure distribution chamber between see the two spring struts lies.
  • pressure and bearing bushings are provided according to the number of spring collars.
  • the shaft can be rotatably or slidably mounted in the or the sealing and bearing bushes. Depending on a sealing and bearing bush is sealed to the of
  • the heat transfer fluid passes through the connecting hole in the hollow bore of the shaft.
  • the hollow bore is preferably designed as an axial blind hole.
  • the hollow bore then has only one opening at one end of the shaft.
  • the connection bore is designed as a through hole through the wall of the hollow bore, so that pressure distribution chamber and hollow bore are fluid-conductively connected to each other.
  • the heat carrier fluid can flow away through the at least one opening of the hollow bore. If the hollow bore is designed as an axial blind hole, then the heat transfer fluid can flow through the opening at one end of the shaft. If the hollow bore is designed as an axial through hole, then the heat transfer fluid can flow out through the openings at the respective ends of the shaft.
  • Fluid flow would be interrupted by the rotary feedthrough according to the invention.
  • the rotary feedthrough according to the invention can also be flowed through in the reverse direction.
  • the fluid then flows in the opposite direction, namely from the at least one opening of the hollow bore through the connection bore in the pressure distribution chamber.
  • the absorber In the case of thermal solar collectors, it is possible, in particular, for the absorber to be fixed in a rotationally fixed manner to the shaft and to be connected in a fluid-conducting manner to at least one opening of the hollow bore. The solar collector can then rotate around the axis of the shaft
  • Rotary feedthrough and be pivoted relative to the pressure distribution chamber without the inflow or outflow of heat transfer medium fluid to or from the absorber would be interrupted. But it is of course also possible that the absorber is secured against rotation relative to the pressure distribution chamber and the pivoting movement relative to the shaft of the rotary feedthrough or an associated component takes place. It is preferred if the sealing and bearing bushes are held in a housing which has an opening for the passage of the shaft and an inlet and outlet opening, wherein the inlet and outlet opening opens into the pressure distribution chamber. In embodiments with more than one spring collar of the pressure distribution chamber is between the spring struts of the shaft. Heat transfer fluid can be introduced into or out of the pressure distribution chamber via the inlet and outlet opening in the housing. Since the sealing and bearing bushes are held in the housing and the shaft opposite the
  • Sealing and bearing bushes is rotatable, the shaft is also rotatably mounted relative to the housing.
  • the pressure distribution chamber and the sealing and bearing bushes are sealed relative to the housing, so that fluid can flow out of the pressure distribution chamber only through the inlet and outlet openings in the housing or the connecting bore of the shaft or can flow into the pressure distribution chamber.
  • a circumferential spring lip may be provided on the housing. The spring lip abuts in the assembled state of the device to a sealing and bearing bush and exerts a biasing force on a sealing and bearing bush in the direction of the adjacent spring collar due to elastic deformation. Since the spring lip is circumferential, the system is also pressure-tight on a sealing and bearing bush. Between a sealing and bearing bush and the adjacent spring lip so a fluid passage is not possible.
  • the region of at least one sealing and bearing bush, which rests flush against one of the spring collars is of spherical design. Due to the crowned design, a small sealing surface is achieved at the same time high surface pressure between the sealing and bearing bush and spring collar. Even with a slight misalignment of the shaft relative to one of the sealing and bearing bushings, a good sealing effect is achieved due to this crowned configuration.
  • breakaway torque denotes the moment required to overcome the static friction between the sealing and bearing bushes and the spring struts or the shaft
  • breakaway torque is particularly advantageous for use in Solarthermischen plants, since the rotation speed around the pivot axis of the solar collectors is very small.
  • the sealing and bearing bushes can be used in one piece as
  • Flange be executed. But it is also possible that they are made in two parts, each with a collar and a socket part. The latter offers the advantage of easier manufacture of the sealing and bearing bushes. However, this can increase the assembly costs of the rotary feedthrough.
  • the spring collars are firmly connected to the shaft disc springs.
  • the connection of the spring struts to the shaft is designed pressure-tight. "Pressure-tight" in the sense of this invention means that a fluid passage between two pressure-tight interconnected elements is not possible.
  • the spring struts can be made in one piece with the shaft, but it is also possible that they are subsequently attached to the shaft, for example by welding.
  • the spring collars are therefore preferably made of corrosion-resistant spring steel. Further preferred it, if the shaft is made of corrosion resistant spring steel. It is further preferred if at least one sealing and bearing bush or at least the collar part of a two-part sealing and bearing bush made of graphite. Graphite is characterized by good self-lubrication properties and heat tolerance.
  • the housing is designed in two parts, wherein the two parts are preferably sealed against each other by a pinch seal made of copper. It is further preferred if the pressure distribution chamber is arranged in one of the two housing parts. This prevents the parting line between the two housing parts from passing through the pressure distribution chamber and forming a possible leak on the pressure distribution chamber.
  • the at least one opening of the hollow bore can be designed as a sealing cone, so that a further component, for example.
  • An absorber or a conduit, pressure-tight manner can be connected to the rotary feedthrough according to the invention. It is further preferred that a threaded or clamping ring is provided at the end of the shaft on which the blind hole is arranged. Alternatively, it is possible that at the end of de the shaft on which the blind hole is arranged, a part of a cutting ring connection is formed.
  • torque supports can be provided in a rotationally fixed manner relative to the distributor chamber and / or rotationally fixed relative to the shaft. About such a torque support loads on the connection areas between rotary feedthrough and other components can be reduced.
  • the system according to the invention comprises a thermal solar collector with an optical element and an absorber.
  • incident solar radiation can be focused on the absorber.
  • the absorber is designed so that it can be flowed through by heat transfer fluid.
  • the thermal solar collector is pivotally mounted about at least one pivot axis.
  • the optical element can be aligned so that it is as perpendicular to the incident solar radiation as possible. If only one pivot axis is provided, it is possible to track the solar collector according to the time of day of the sun. If the solar collector can also be pivoted about a second pivot axis, a compensation of the seasonal solar movement is also possible.
  • the absorber can be designed as an elongated absorber tube.
  • the optical element may be a linear Fresnel lens which focuses the incident solar radiation onto the absorber tube. A linear one Fresnel lens does not focus the incident solar radiation on one point but along a focus line. The absorber tube is then arranged along this focal line.
  • the system according to the invention further comprises a rotary feedthrough according to the invention.
  • the absorber pipe is connected to the rotary feedthrough, either rotationally fixed and fluid-conducting with the hollow bore or with the pressure distribution chamber.
  • the shaft of the rotary feedthrough is arranged coaxially with one of the at least one pivot axis.
  • heat transfer fluid is supplied to the absorber of the solar collector or can run off, regardless of the position around the at least one pivot axis of the thermal solar collector.
  • the heat transfer fluid can, for example, pass from the pressure distribution chamber via the connection bore and the hollow bore into one end of the absorber tube. If a further rotary feedthrough is provided at the opposite end of the absorber tube, the heat transfer fluid can flow away via this additional rotary feedthrough.
  • the thermal solar collector is thus pivotable about the pivot axis, without the supply or the outflow of heat transfer fluid would be interrupted.
  • This additional device stored in the heated, discharged from the absorber tube heat transfer fluid stored energy can be converted into usable energy.
  • This additional device may be a heat exchanger or to be a turbine.
  • the cooled in the additional device heat transfer fluid can then be supplied to the absorber again. It is preferred if two rotary unions are provided per pivot axis. The supply of heat transfer fluid can then be ensured via a rotary feedthrough, while the heat transfer fluid is discharged from the absorber via the other rotary feedthrough.
  • the rotary unions can also fulfill the function of supporting the solar thermal collector around a pivot axis. Separate bearings are then no longer required.
  • Fig. 1 shows a first embodiment of an inventive
  • FIG. 2 is a sectional view through the first embodiment along section line II-II of Figure 1; 3 shows a section through the first embodiment along the section line III-III of Figure 1; 4 shows a sectional illustration through the first embodiment along the section line IV-IV from FIG. 1; 5 is a sectional view of a second embodiment of a rotary feedthrough according to the invention;
  • FIG. 6 is a sectional view of a third embodiment of a rotary feedthrough according to the invention.
  • FIG. 7 shows a plan view of the third embodiment according to FIG. 6; FIG. and
  • FIG. 8 shows a schematic representation of a system according to the invention.
  • Figures 1 to 4 a first embodiment of a rotary feedthrough 1 according to the invention is shown.
  • Figure 1 shows a side view of the rotary feedthrough 1
  • Figure 2 is a sectional view of the rotary feedthrough 1 along the section line II-II shown in Figure 1.
  • the rotary feedthrough 1 comprises a shaft 10 which is rotatably mounted in a housing 20.
  • the rotary feedthrough 1 is designed so that - regardless of the position of the shaft 10 relative to the housing 20 - heat transfer fluid in the liquid or gaseous state from an inlet and outlet port 21 in the housing 20 to an opening 11 on an end face 12 of the shaft 10 (or conversely) can flow.
  • a hollow bore 13 is provided.
  • the hollow bore 13th is aligned concentrically with the axis of the shaft 10 and designed as a blind hole.
  • a pressure distribution chamber 14 is provided, which surrounds the shaft 10 in an annular manner.
  • the pressure distribution chamber 14 is limited in the axial direction of the shaft 10 by two spring collars 15.
  • the spring struts 15 are formed integrally with the shaft 10 and thus firmly and pressure-tightly connected thereto.
  • connection bore 16 is provided in the area of the pressure distribution chamber 14.
  • the connection bore 16 is a through-bore through the wall of the hollow bore 13. Through the connection bore 16, the hollow bore 13 and pressure-distribution chamber 14 are connected to one another in a fluid-conducting manner.
  • the opening 11 on the one end 12 of the shaft 10 is connected to the pressure distribution chamber 14 so that heat transfer fluid from the pressure distribution chamber 14 to the opening 11 on one end face 12 of the shaft 10 can pass.
  • a reverse flow direction of the heat transfer fluid is of course possible.
  • the spring struts 15 can - as shown - be designed in one piece with the shaft. But you can also made separately from the shaft 10 and then with the shaft 10 pressure-pressure-tight, eg. By welding, be connected.
  • the spring collars 15 are designed so that they can be elastically pivoted or deformed in the axial direction of the shaft 10.
  • the shaft 10 is mounted in two sealing and bearing bushes 30. Between sealing and bearing bushes 30 and the shaft 10 is a sliding bearing. In each case one of the sealing and bearing bushes 30 is flush against the side facing away from the Druckverteiler- 14 side 17 of a spring collar 15 and is biased against this. Between a sealing and bearing bush 30 and the adjacent spring collar 15 so there is a contact pressure. By the voltage applied to the spring collar 15 part of the sealing and bearing bush 30 prevents fluid between the sealing and bearing bush 30 and shaft 10 can pass.
  • the sealing and bearing bushes 30 are designed as flanged bushings, wherein the voltage applied to one side 17 of a spring collar 15 waist section 31 of the sealing and Lagerb chse 30 is configured crowned. Due to the crowned design of the collar section 31 of the sealing and bearing bushes 30 creates a small sealing surface 32 between a spring collar 15 and a sealing and bearing bushing 30. Due to the small sealing surface 32 there is a high surface pressure, which is a good sealing effect Episode has. Due to the crowned design of the collar section 31 of the sealing and bearing bushings 30, a high sealing effect is achieved even when there is a slight skewed position of the shaft 10 relative to a sealing and bearing bush 30.
  • the sealing and bearing bushes 30 are rotatably supported in the housing 20.
  • the housing 20 comprises a first and a second housing part 22, 23, which are sealed with a metallic 0-ring (for example, a pinch seal 24 made of copper) against each other.
  • the pressure distribution chamber 14 is arranged in a 22 of the two housing parts 22, 23.
  • the parting line 28 between the two housing parts 22, 23 thus does not extend through the pressure distribution chamber 14.
  • the parting line 28 therefore does not form a possible leak at the pressure distribution chamber 14.
  • the above-mentioned inlet and outlet opening 21 is provided in the first housing part 22 and arranged so that it is in the assembled state of the rotary feedthrough 1 in connection with the pressure distribution chamber 14.
  • the inlet and outlet opening 21 is provided with an internal thread 25.
  • the housing 20 also has an opening 27 for the passage of the shaft 10.
  • the shaft 10 and the spring collars 15 connected in one piece are made of corrosion-resistant spring steel. provides. This ensures that even in extreme applications with temperatures of over 450 ° C and high pressures up to 150 bar, the spring collars 15 can still be deformed elastically. The sealing effect between Federbün- the 15 and sealing and bearing bushes 30 is guaranteed even in such extreme applications.
  • the sealing and bearing bushes 30 are made of graphite. As a result, a lower friction between the sealing and bearing bushes 30 and the shaft 10 is achieved, which has a low breakaway torque of the rotary feedthrough 1 result.
  • the opening 11 of the blind hole 13 is designed as a sealing cone.
  • the shaft 10 has an external thread 18.
  • a threaded ring 40 is fixed, which surrounds the shaft 10 annular and regularly distributed over its circumference through holes 41 having internal thread.
  • the threaded ring 40 can be against the shaft 10 non-rotatable, fastened relative to the housing 20 rotatable component. Due to the design of the blind hole 11 as a sealing cone can be a pressure-resistant, fluid-conducting connection between a rotatable member and the shaft 10 accomplish.
  • the threaded ring 40 is shown in detail in Figure 3 as a sectional view along the section line III-III of Figure 1.
  • the threaded ring 40 is screwed onto the external thread 18 of the shaft 10 and secured by a threaded pin 42 against unwanted release of the shaft 10. He is so rotatably connected to the shaft 10.
  • the threaded ring 40 has uniformly over the circumference and around the opening for the shaft 10 distributed holes with internal thread 41. At these holes with internal thread 41, a component on the threaded ring 41 and thus with the shaft 10 can be connected by screws or bolts.
  • the component is preferably designed so that it is also fluid-conductively connected to the opening 11 on the end face 12 of the shaft 10 during attachment to the threaded ring 41.
  • a torque support 43 is further provided, with the loads on the bore with internal thread 41 or inserted therein screws or bolts due to torques about the axis of the shaft 10 can be greatly reduced.
  • FIG 4 shows a sectional view of the housing 20 according to the section line IV-IV of Figure 1 is shown.
  • the illustrated first housing part 22 has distributed over the circumference and arranged around the axis of the shaft 10 holes 26.
  • the holes 26 are equipped with an internal thread.
  • the second housing part 23 can be fixedly connected to the first housing part 22.
  • FIG. 5 shows a second exemplary embodiment of a rotary feedthrough 1 according to the invention.
  • the rotary feedthrough 1 from FIG. 2 is largely identical to the rotary feedthrough 1 from FIGS. 1 to 4, for which reason reference is made to the statements there. The following will be only the differences between the two embodiments.
  • two connecting bores 16 are provided in the exemplary embodiment shown in FIG.
  • the two connecting bores 16 lie on a common axis and can be produced in a production step as a through-bore through the shaft 10.
  • the flow resistance of the rotary feedthrough 1 can be reduced.
  • the sealing and bearing bushes 30 are made in two parts and that with a socket part 33 and a collar part 34.
  • the bushing parts 31 are the sliding bearing of the shaft 10 in the housing 20.
  • the collar parts 32 of the sealing and bearing bushes 30 are each the side facing away from the pressure distribution chamber 14 side of one of the spring collars 15 of the shaft.
  • waistband member 32 prevents fluid between the waistband 32 and the shaft 10 can pass.
  • a sealing of the pressure distribution chamber 14 with respect to the outside of the shaft 10 or the environment is achieved.
  • the region of the sealing and bearing bushes 30 and the collar parts 32 which bears against one of the spring collars 15, designed crowned.
  • FIG. 5 furthermore shows how a further component 90 can be fastened to the shaft 10.
  • the component 90 has a fluid channel 91, whose one end 92 in the Sealing cone of the opening 11 of the hollow bore 13 of the shaft 10 can be inserted.
  • the component 90 further has a circumferential projection 93, which is engaged behind by a clamping ring 94.
  • the clamping ring 94 is connected via screws 95 which engage in the holes with internal thread 41 of the threaded ring 40, with the threaded ring 40 and thus the shaft 10 rotatably connected.
  • fluid can pass from the inlet and outlet opening 21 in the housing 20 via the pressure distribution chamber 14, the connection bores 16 and the hollow bore 13 heat transfer fluid into the fluid channel 91 of the component 90 with the rotary feedthrough 1 according to the invention.
  • a reverse flow direction is possible.
  • threaded ring 40 is connected to the component 90 and an associated clamping ring engages behind a projection on the shaft 10 (not shown).
  • FIGs 6 and 7 a third embodiment of a rotary feedthrough 1 according to the invention is shown.
  • the rotary feedthrough 1 of Figures 6 and 7 is identical in many parts to the rotary feedthrough according to Figures 1 to 4, and 5, which is why reference is made to the statements there.
  • particular attention is paid to the differences between the exemplary embodiments. It is also self- understandable that individual aspects, such. Example, the configuration of the shaft 10 for connection to other components 90 (see Fig .. 5) are interchangeable between the individual embodiments.
  • the rotary feedthrough 1 according to FIGS. 6 and 7 differs mainly in that only one spring collar 15 is provided on the shaft 10. With this spring collar 15, the pressure chamber 14 is limited in the axial direction on one side. The limitation of the pressure chamber 14 in the axial direction on the other side is ensured by the housing 20 and the first housing part 22.
  • the sealing and bearing bush 30 is in this case made in two parts, wherein the bushing part 33 of the sliding bearing of the shaft 10 is used while the collar part 34 does not necessarily contribute to the storage of the shaft 10.
  • the collar part 34 is, as described below, pressed with a bias to the spring collar 15, so that between the spring collar 15 and waistband 34 no liquid can pass through.
  • a circumferential spring lip 29 is provided on the second housing part 23.
  • the spring lip 29 is in the illustrated assembled state of the rotary feedthrough 1 on the collar part 34 of the sealing and bearing bush 30 and exerts a biasing force on the collar part 34 in the direction of the spring collar 15 due to elastic deformation. Since the spring lip 11 is also circumferential, the system is on the collar part 34 of the sealing and bearing bush 30 pressure-tight. So there can be no liquid keits between the collar portion 34 of the bearing bush 30 and the spring lip 29 abutting thereon pass.
  • the shaft 10 is still stored in a guide bush 40 in addition to the socket part 33 of the sealing and bearing bush 30.
  • a spacer 41 in the form of a ball is also provided, with which the distance between the shaft 10 and the housing part 22 is fixed. The shaft 10 is then held in position due to the bias on the spring collar 15 and the spacer 41, while remaining naturally rotatable.
  • the collar part 34 of the sliding and bearing bush 35 is made of graphite, the bushing part 33 and the guide bushing 40 can also be made of other material.
  • the bushing part 33 and / or the guide bushing 40 may alternatively be designed as rolling bearings.
  • the rotary feedthrough 1 according to the invention is suitable both for the rotary feedthrough of liquid heat transfer fluid and of heat transfer fluid in gaseous form. The latter is particularly required for use with thermal solar collectors in which an initially liquid heat transfer medium is heated to such an extent that a phase change takes place towards the gas form.
  • a system 100 with a corresponding thermal solar collector 101 is shown in FIG.
  • the system 100 includes a solar thermal collector 101 having an optical element 102 and an absorber 103.
  • the optical element 102 is a linear fresnel lens perpendicular to the optical element 102 concentrating incident solar radiation on a focus line.
  • the absorber 103 is arranged in the focal line of the optical element 102.
  • the absorber 103 is designed as an absorber tube through which heat transfer fluid can flow. The heat transfer fluid flowing through the absorber 103 is heated by the solar radiation focused on the absorber 103.
  • the solar thermal collector 101 is pivotable about a first and a second pivot axis 201, 202. Due to the pivotability about the two pivot axes 201, 202 a biaxial tracking of the solar thermal collector 101 to the sun is possible.
  • the thermal solar collector 101 can always be aligned with the sun so that the sun's rays impinge perpendicularly on the optical element 102.
  • Swivel axes 201, 202 is flowed through by heat transfer fluid.
  • the system 100 comprises rotary unions 1 according to the invention.
  • FIGS. 1 to 5 For an explanation of the rotary unions according to the invention, reference is made to FIGS. 1 to 5 and the above explanations.
  • two rotary unions 1 are provided, which are aligned with their respective shaft 10 coaxial with the pivot axis 201 and with the end faces 12 of the respective shafts 10 opposite.
  • the thermal solar collector 101 is fixedly connected to the shafts 10 of the rotary feedthrough 1. Due to the rotatable bearings of the shafts 10 in the housings 20 of the rotary unions 1, the solar collector 101 is pivotable relative to the housings 20 of the rotary unions 1 about the pivot axis 201. An additional storage of the solar collector 101 about the pivot axis 201 is not required.
  • the respective openings 11 in the shafts 10 of the rotary leadthrough 1 are connected in a fluid-conducting manner via tubes 104 to one end of the absorber 103. It is therefore possible that heat transfer fluid from the inlet and outlet 21 of a rotary feedthrough 1 passes through the rotary feedthrough 1 and through the pipes 104 to the absorber 102, flows through it, and again through pipes 104 and the other rotary feedthrough 1 to the outlet opening 21 of the other Rotary union 1 flows. This flow of heat transfer fluid is independent of the position of the solar collector 101 about the pivot axis 201 possible.
  • the housing 20 of the rotary feedthrough 1 are fixedly mounted on a frame 105.
  • the frame 105 is rotatably supported about the pivot axis 202.
  • the rotary feedthroughs 1 are aligned with their shaft 10 coaxial with the pivot axis 202 and are opposite to the respective end faces 12.
  • the inlet and outlet openings 21 of the rotary feedthroughs 1 along the pivot axis 201 are connected via pipe 106, each having an opening 11 on the end faces 12 of the shaft 10 of the rotary feedthrough 1.
  • the frame 105 - and thus the pivot axis 201 and the thermal solar collector 101 - can be adjusted around the pivoting axis 202 pivot. Due to the rotary feedthroughs 1 along this pivot axis 202, heat transfer fluid can arrive independently of the position of the solar collector 101 about the pivot axes 201, 202 to the absorber 103 or be led away from it.
  • the housing 20 of the rotary feedthrough 1 about the pivot axis 202 are connected to a local infrastructure 300.
  • the infrastructure 300 includes a pump 301, a turbine 302, and a piping system 304.
  • heat transfer fluid is conveyed through the piping system 304 to an inlet opening 21 of a rotary feedthrough 1 about the pivot axis 202.
  • the rotary feedthrough 1 is - as explained above with reference to FIGS. 1 to 5 - flowing through, so that the heat transfer fluid passes via the pipe connection 106 to one of the rotary feedthroughs 1 about the pivot axis 201.
  • the heat transfer fluid also flows through this rotary feedthrough 1 and passes via the pipe 104 into the absorber 103. In the absorber 103, it is so strongly heated by the solar radiation focused on the absorber 103 with the optical element 102 that it changes its phase and becomes gaseous.
  • the gaseous heat transfer medium is discharged via the pipes 104 from the absorber 103 and passes through the rotary unions 1 and the pipes 106 back into the piping system 303 of the local infrastructure 300.
  • the gaseous heat transfer medium is then fed to the turbine 302, where it is for generating electrical energy is used. During this process, the heat transfer medium cools down again so strongly that it changes its phase again and is again in liquid form.
  • the liquid ge heat transfer medium can then be supplied to the absorber 103 via the pump 301 as described.
  • the system 100 according to the invention comprises the rotary unions 1 according to the invention, it is possible that the absorber 103 is flowed through by heat transfer fluid, regardless of which position the thermal solar collector 100 occupies about the pivot axes 201, 202.

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  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

L'invention concerne un passage tournant (1) pour vapeur surchauffée, destiné en particulier à être utilisé dans des installations thermo-solaires (100). L'invention concerne en outre un système (100) d'une installation thermo-solaire, comprenant un capteur solaire thermique et un passage tournant selon l'invention. Le passage tournant (1) selon l'invention pour fluide caloporteur à l'état liquide ou gazeux comprend un arbre (10) doté d'un trou creux (13), d'un espace de répartition de pression (14) entourant l'arbre (10) de manière annulaire et délimité dans la direction axiale par au moins une bride de ressort (15) reliée fixement à l'arbre (10). Dans la zone de l'espace de répartition de pression (14), un trou de liaison (16) est ménagé dans la paroi du trou creux (13). L'invention concerne en outre au moins un coussinet d'étanchéité et de palier (30), chaque coussinet d'étanchéité et de palier (30) reposant à fleur du côté de la bride de ressort (15) respectivement adjacente qui est opposé à l'espace de répartition de pression (14), et étant précontraint contre celui-ci.
PCT/EP2011/055598 2010-04-12 2011-04-11 Passage tournant pour vapeur surchauffée WO2011128284A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202010004847.8 2010-04-12
DE201020004847 DE202010004847U1 (de) 2010-04-12 2010-04-12 Drehdurchführung für Heißdampf

Publications (1)

Publication Number Publication Date
WO2011128284A1 true WO2011128284A1 (fr) 2011-10-20

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PCT/EP2011/055598 WO2011128284A1 (fr) 2010-04-12 2011-04-11 Passage tournant pour vapeur surchauffée

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DE (1) DE202010004847U1 (fr)
WO (1) WO2011128284A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107061899A (zh) * 2017-01-17 2017-08-18 广州富森环保科技股份有限公司 外驱动旋转接头
CN110508544A (zh) * 2019-09-23 2019-11-29 浙江苏强格液压股份有限公司 一种机床用清洗装置

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2920710A (en) * 1956-12-17 1960-01-12 George E Howard Vehicle having a solar steam generator
US3627355A (en) * 1969-05-23 1971-12-14 Robert R Reddy Fluidtight swivel joint
US4192559A (en) * 1978-04-28 1980-03-11 Koppers Company, Inc. Rotary union
US4323268A (en) * 1978-06-05 1982-04-06 E-Systems, Inc. Rotary pipe joint
FR2551832A1 (fr) * 1983-09-09 1985-03-15 Pinay Jack Perfectionnements apportes aux raccords tournants

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2920710A (en) * 1956-12-17 1960-01-12 George E Howard Vehicle having a solar steam generator
US3627355A (en) * 1969-05-23 1971-12-14 Robert R Reddy Fluidtight swivel joint
US4192559A (en) * 1978-04-28 1980-03-11 Koppers Company, Inc. Rotary union
US4323268A (en) * 1978-06-05 1982-04-06 E-Systems, Inc. Rotary pipe joint
FR2551832A1 (fr) * 1983-09-09 1985-03-15 Pinay Jack Perfectionnements apportes aux raccords tournants

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107061899A (zh) * 2017-01-17 2017-08-18 广州富森环保科技股份有限公司 外驱动旋转接头
CN110508544A (zh) * 2019-09-23 2019-11-29 浙江苏强格液压股份有限公司 一种机床用清洗装置

Also Published As

Publication number Publication date
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