EP3237729B1 - Expansionsmaschine mit wellendichtring und ventil - Google Patents

Expansionsmaschine mit wellendichtring und ventil Download PDF

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Publication number
EP3237729B1
EP3237729B1 EP15784670.0A EP15784670A EP3237729B1 EP 3237729 B1 EP3237729 B1 EP 3237729B1 EP 15784670 A EP15784670 A EP 15784670A EP 3237729 B1 EP3237729 B1 EP 3237729B1
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EP
European Patent Office
Prior art keywords
valve
expansion machine
space
membrane
control
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.)
Active
Application number
EP15784670.0A
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German (de)
English (en)
French (fr)
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EP3237729A1 (de
Inventor
Steffen Buhl
Nadja Eisenmenger
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP3237729A1 publication Critical patent/EP3237729A1/de
Application granted granted Critical
Publication of EP3237729B1 publication Critical patent/EP3237729B1/de
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Anticipated expiration legal-status Critical

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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
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/001—Preventing or minimising internal leakage of working-fluid, e.g. between stages for sealing space between stator blade and rotor
    • 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
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/003—Preventing or minimising internal leakage of working-fluid, e.g. between stages by packing rings; Mechanical seals
    • 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
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/02—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type
    • 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
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/04—Blade-carrying members, e.g. rotors for radial-flow machines or engines
    • F01D5/043—Blade-carrying members, e.g. rotors for radial-flow machines or engines of the axial inlet- radial outlet, or vice versa, type
    • F01D5/046—Heating, heat insulation or cooling means

Definitions

  • the invention relates to an expansion machine with a shaft seal and a valve.
  • the expansion machine can be used for example for waste heat utilization of an internal combustion engine.
  • Expansion machines with a shaft sealing ring for sealing a working medium flowing in the expansion machine are known from the prior art, for example from the published patent application DE 10 2012 222 010 A1 .
  • the expansion machine according to the invention comprises a transmission with an output shaft and a shaft seal cooperating with the output shaft.
  • the expansion machine has an inflow region and an outflow region and, during operation, flows through a working medium, wherein compressed working medium flows out of the outflow region into the inflow region and relaxed working medium.
  • the shaft sealing ring separates a gear chamber or valve space filled with working medium from an ambient space or from a further machine, for example from a generator.
  • the expansion machine is operated in overpressure, that is, the relaxed working fluid has a pressure that is above atmospheric pressure.
  • the sealing lip is then arranged in such a way to the output shaft, that an overpressure in the expansion machine to the ambient space, which is under atmospheric pressure, is reliably sealed.
  • the expansion machine according to the invention with a shaft seal and a valve has the advantage that they can be operated without leakage both in the overpressure and in the vacuum operation and the shaft seal achieved in all operating conditions a good sealing effect.
  • the expansion machine according to the invention thus has a much wider range of operating conditions in which it can be used without leakage.
  • the expansion machine comprises an output shaft and a shaft seal cooperating with the output shaft.
  • the expansion machine has an inflow region and an outflow region.
  • the expansion machine is flowed through with a working medium, wherein in operation of the expansion machine compressed working fluid flows into the inflow and relaxed working fluid from the outflow.
  • the shaft seal separates one with working fluid filled valve space from an ambient space.
  • a valve is arranged, and the pressure in the valve chamber is regulated by the valve.
  • the pressure acting on the shaft sealing ring on the side of the expansion machine can be regulated.
  • the pressure on the shaft sealing ring on the side of the expansion machine is always at least as great as on the side to the environment or to the surrounding space.
  • the tightness function of the shaft seal is thus ensured over all operating conditions of the expansion machine, even if it is operated in negative pressure. There is no leakage of the working medium in the surrounding space.
  • the expansion machine comprises a housing, wherein the valve is arranged in the housing.
  • the valve does not require its own housing, but can be arranged in a cost-effective and space-saving manner in the housing of the expansion machine.
  • the inflow is hydraulically connected to the valve chamber through a throttle.
  • the valve space By connecting the valve space to the inflow area, the valve space can be regulated by the valve to the pressure level of the inflow area, which pressure level is higher than the pressure level of the surrounding space; This achieves a good sealing effect of the shaft seal.
  • the throttle When the valve is open, the throttle causes the valve chamber not to be raised to the pressure level of the inflow region, which is also not required for the valve chamber in this operating state.
  • valve chamber is not connected to the inflow region but to a region which lies between inflow and outflow region.
  • the valve comprises an inlet channel, an outlet channel, and a closing body.
  • the closing body is preferably spherical.
  • the closing body cooperates with a valve seat.
  • the inlet channel opens into the valve chamber or leads out of this.
  • the closing body when engaged with the valve seat, closes a hydraulic connection from the inlet channel to the outlet channel, and opens the hydraulic connection when lifted from the valve seat. By opening and closing the hydraulic connection, the pressure in the valve chamber is controlled in a simple manner.
  • the outlet channel is hydraulically connected at least indirectly to the outflow region.
  • the pressure in the valve chamber is regulated with the valve open to the pressure level of the outflow region, which is usually the lowest pressure level within the expansion machine. This minimizes stress on the shaft seal when the valve is open.
  • the valve comprises a control room and a regulatory channel opening into the control room. This allows the valve to be pneumatically or hydraulically controlled or even controlled.
  • control channel is hydraulically connected to the ambient space or with the atmosphere. This is particularly advantageous when applied to the side facing away from the expansion of the shaft seal the pressure of the ambient space or the atmospheric pressure, because then exactly this pressure can also be used as a controlled variable for the valve. Furthermore, the control with atmospheric pressure or with the pressure of the ambient space is very cost-effective, since a volume having a corresponding pressure level, anyway in the expansion machine or its attachments or just in the environment is present.
  • the valve comprises a membrane, and the control chamber adjoins the membrane. This allows the control room Media-tight, in particular to the inlet channel and the outlet channel to be separated.
  • the membrane is made of a metal, in particular of a thin metal, or of an elastomer.
  • the membrane is comparatively easily deformable and the hydraulic connection from inlet channel to outlet channel accordingly also has a sufficiently large cross section when the valve is open.
  • the membrane acts on its opposite side of the control room at least indirectly together with the closing body.
  • the geometries and materials of membrane and closing body can be selected as best as possible with regard to their functions: the membrane is comparatively elastic and the closing body is wear-resistant and comparatively stiff.
  • the membrane cooperates with the interposition of an auxiliary piston with the closing body, wherein the auxiliary piston is preferably longitudinally movably guided in a guide sleeve.
  • the auxiliary piston has the function of performing the longitudinal movement during opening and closing of the valve with as little friction as possible, for example in cooperation with the guide sleeve.
  • the power transmission between the auxiliary piston and closing body can be designed so that the closing body when closing the valve very well centered in the valve seat, for example, by convex designs of the contact surfaces of the auxiliary piston and closing body.
  • an annular chamber is formed at least partially surrounding the inlet channel radially.
  • the outlet channel opens into the annular chamber, wherein the valve seat is arranged between the inlet channel and the annular chamber.
  • the pressures from the outlet channel or the annular chamber and from the inlet channel act in the same direction on the closing body. If the outlet channel is under a lower pressure than atmospheric pressure, then the closing body is loaded with a comparatively small resulting hydraulic force by the working medium for this operating state. The closing body is therefore against the valve seat pressed. Since the valve seat is formed between the annular chamber and the inlet channel, so can also be set over the width of the valve seat, a throttle length for the operating state of the opened valve.
  • the closing body is a membrane, preferably made of an elastomer or a thin metal.
  • the membrane can be simple, for example, disc-shaped, constructed and is therefore inexpensive to use.
  • a control chamber is also formed here on the opposite side of the valve seat of the membrane, which opens into a control channel.
  • the control room can thus be connected via the control channel to a volume having a control pressure, for example to the atmosphere or the surrounding space.
  • the closing body or the membrane is then acted upon from one side with this control pressure and from the other side partially with the pressure of the annular chamber or the Ausström Schemes and partially with the pressure of the inlet channel and the valve chamber.
  • the opening and closing of the valve can be regulated, for example as follows: If the pressure in the annular chamber falls below the pressure of the control chamber, the membrane is pressed into the valve seat and the Pressure holding function for the valve chamber thus activated.
  • control space between the membrane and a lid is formed.
  • the lid also preferably braces the membrane at its periphery, for example by pressing the membrane against the housing of the valve or the expansion machine.
  • the membrane is fixed on the circumference within the valve. The opening and closing of the valve thus takes place by a movement of the non-strained surfaces of the membrane.
  • control channel is formed in the lid, wherein the control channel is preferably hydraulically connected at its end opposite the control room end with the surrounding space or with the atmosphere.
  • control channel can be produced inexpensively by a simple hole in the lid.
  • control channel can alternatively be performed space-saving through a common housing of expansion machine or valve and ambient space.
  • the expansion machine according to the invention is arranged in a waste heat recovery system, in particular an internal combustion engine.
  • the waste heat recovery system comprises in the flow direction of the working medium, a pump, an evaporator, the expansion machine and a condenser.
  • the outlet channel is hydraulically connected at least indirectly to the condenser.
  • the outflow region of the expansion machine is usually hydraulically connected to the condenser and thus has the same pressure as the condenser.
  • the outlet channel is then connected to this already existing pressure level.
  • the waste heat recovery system is preferably not operated at a single operating point, but at very different operating points, since the internal combustion engine is operated at different operating points. This makes it very beneficial for the overall efficiency of the waste heat recovery system when the expansion machine can run in both positive pressure and negative pressure modes.
  • the expansion machine according to the invention is therefore particularly suitable for this purpose.
  • Fig.1 shows schematically an expansion machine 20 according to the invention within a waste heat recovery system 1, wherein only the essential areas are shown.
  • a pump 30, an evaporator 31, an expansion machine 20 and a condenser 32 are arranged in the flow direction of a working medium.
  • the evaporator 31 is also connected to an exhaust pipe, not shown, of an internal combustion engine, not shown.
  • Liquid working fluid is compressed by the pump 30 and conveyed to the evaporator 31, where it is vaporized by the heat energy of the exhaust gas of the internal combustion engine. Subsequently, the vaporized working medium is supplied to the expansion machine 20, where it is expanded while releasing mechanical energy. Subsequently, the working fluid in the condenser 32 is liquefied again.
  • the expansion machine 20 may be, for example, a turbine, a piston expander or a Scrollexpander.
  • the expansion machine 20 is a turbine with an impeller 23 and an output shaft 24.
  • the expansion machine 20 further comprises according to the invention an inflow region 21, an outflow region 22, a shaft seal 25, a valve 10, a valve chamber 11 and a partition wall 27.
  • the compressed working medium flows through the inflow region 21 and the outflow region 22 and is thereby expanded.
  • the thereby released mechanical energy is transmitted through the output shaft 24 to one or more recyclers, not shown, for example, a turbocharger, a transmission or a generator.
  • the inflow region 21 is hydraulically connected at least indirectly via a throttle 9 to the valve space 11.
  • the valve 10 opens and closes a hydraulic connection from the valve space 11 to the discharge area 22 and to the condenser 32, respectively.
  • the valve space 11 is sealed by the dividing wall 27 to the discharge area and by the shaft sealing ring 25 to an ambient space 40.
  • the ambient space 40 may be, for example, a gear chamber or an atmospheric space.
  • the partition 27 is in the Fig.1 shown between the discharge area 22 and the valve space 11, but need not necessarily be arranged so. It is only intended to clarify that there is only a hydraulic inflow via the throttle 9 and a hydraulic outflow via the valve 10 into the valve space 11 and that the valve space 11 is otherwise separated from the inflow area 21 and the outflow area 22. Furthermore, the arrangement of the valve chamber 11 depends on which side the output shaft 24 is led out of the expander 20, since usually at this point the shaft seal 25 is arranged and accordingly adjacent the valve chamber 11 must be arranged.
  • valve 10 may also be arranged in the partition wall 27; or the partition wall 27 may be disposed between the inflow region 21 and the valve space 11 and the throttle 9 may then be formed in the partition wall 27.
  • the various embodiments are also the pressures in Einström Scheme 21, outflow 22, valve chamber 11 and ambient space 40; this will be discussed in more detail later.
  • Fig.2 schematically shows an embodiment of the expansion machine 20, wherein only the essential areas are shown.
  • the expansion machine 20 is designed as a radial turbine and comprises a housing 26 in which the valve 10 is arranged.
  • the inflow region 21, the outflow region 22 and the valve space 11 are formed in the housing 26.
  • partition 27 thus be seen from a composite of impeller 23 and output shaft 24.
  • the valve space 11 is advantageously formed on a rear side 23 b of the impeller 23, that is on the side facing away from the actual flow path of the working medium through the impeller 23 side.
  • an overpressure prevailing in the valve chamber 11 with respect to the outflow region 22 can bring about at least partial compensation of the pressures or forces acting on the impeller 23 in the axial direction.
  • the shaft seal 25 seals the valve chamber 11 to the ambient space 40 by a arranged on the shaft sealing ring 25 sealing lip 25 a with the output shaft 24 cooperates.
  • the transition from the inflow region 21 to the outflow region 22 is not a clearly defined limit.
  • the working fluid is expanded as it flows through the impeller 23 on the front side 23a, whereby a pressure gradient over the impeller 23 or over the front side 23a is created by the relaxation, so that here the inflow 21 is not clearly separated from the discharge 22, but a Art forms a mixing region in which the pressure falls from an inlet pressure upstream of the expansion machine 20 to an outlet pressure downstream of the expansion machine 20.
  • valve chamber 11 is hydraulically connected to the inflow region 21 via the throttle 9.
  • valve space 11 may also be connected to the mixing area.
  • the valve 10 comprises an inlet channel 12, an outlet channel 13, a spherical closing body 15 and a closing spring 16.
  • the inlet channel 12 opens into the valve chamber 11.
  • the outlet channel 13 opens advantageously in a region having a lower pressure than the valve chamber 11, the Example in the discharge area 22.
  • the closing body 15 cooperates with a formed on the housing 26 valve seat 26a and thereby opens and closes a hydraulic connection from the inlet channel 12 to the outlet channel 13.
  • the closing spring 16 presses the closing body 15 against the valve seat 26a. By the closing spring 16 thus a minimum pressure in the valve chamber 11 can be adjusted.
  • FIG. 3 shows an embodiment of the valve 10, wherein 3a the valve 10 in the closed position and 3b the valve 10 in the open position shows.
  • the valve 10 is disposed in the housing 26 of the expansion machine 20. Alternatively, however, the valve 10 may be disposed in any other housing.
  • the intake passage 12 is formed in an intake passage 12a and the exhaust passage 13 is formed in an exhaust passage 13a.
  • the inlet pipe 12 a and the outlet pipe 13 a are pressed or screwed into the housing 26. Both the inlet channel 12 and the outlet channel 13 open into an interior 50 formed in the housing 26.
  • the valve seat 26a is arranged between inlet line 12a and outlet line 13a on the housing 26, with which the closing body 15 arranged in the interior 50 cooperates.
  • the closing body 15 is pressed in the closed position of the valve 10 by a diaphragm 51 which acts like a leaf spring in this embodiment, with the interposition of an auxiliary piston 52 against the valve seat 26a ( 3a ). In the open position of the valve 10, the closing body 15 is lifted off the valve seat 26a and thus opens the hydraulic connection from the inlet channel 12 to the outlet channel 13 ( FIG. 3b ).
  • the auxiliary piston 52 is longitudinally movable by a fixedly connected to the housing 26 guide sleeve 53, ie in the opening and closing direction of the closing body 15, guided in the housing 26.
  • the membrane 51 is connected to a clamping piece 54 at its edge fixed to the guide sleeve 53 and thus also indirectly to the housing 26.
  • a cover 55 is screwed to the housing 26 and thereby presses the clamping piece 54 with the interposition of the edge of the diaphragm 51 against the guide sleeve 53; the membrane 51 is thus braced at its periphery with the housing 26.
  • the contact between Guide sleeve 53 and closing body 15 may for example be designed convex to optimize the self-centering of the closing body 15 in the valve seat 26a.
  • control chamber 60 is formed between membrane 51, clamping piece 54 and cover 55.
  • the membrane 51 seals the control chamber 60 against the interior 50.
  • the control room 60 opens a control channel 14.
  • the control channel 14 may, as in the embodiment of Figure 3 to be a bore in the lid 55. However, the control channel 14 may for example also be formed in a control line which is screwed or pressed into the cover 55 or in the housing 26.
  • the guide sleeve 53 and / or the clamping piece 54 may also be omitted.
  • the corresponding functions-clamping the membrane 51 and guiding the auxiliary piston 52 - are then integrated, for example, in the two components housing 26 and cover 55.
  • control channel 14 with the atmosphere, the inlet channel 12 with the valve chamber 11 and the outlet channel 13 with the discharge area 22 are hydraulically connected.
  • FIG. 4 shows a further embodiment of the valve 10, wherein only the essential areas are shown.
  • the valve 10 is disposed in the housing 26 of the expansion machine 20. Alternatively, however, the valve 10 may be disposed in any other housing.
  • the inlet channel 12 and the outlet channel 13 are arranged.
  • a diaphragm 51 ' is clamped between the housing 26 and the lid 55, in which embodiment the diaphragm 51' has the function of the closing body.
  • the lid 55 is bolted to the housing 26.
  • In the cover 55 of the control channel 14 is formed. Between the cover 55 and the membrane 51 'of the control chamber 60 is formed, in which the control channel 14 opens.
  • the diaphragm 51 At the side opposite the control chamber 60, the diaphragm 51 'seals the inlet channel 12 in the closed position of the valve 10, by cooperating with the valve seat 26a formed on the housing 26. Surrounding the inlet channel 12 at least partially radially, an annular chamber 61 is formed in the housing 26, into which the outlet channel 13 opens. In the closed position of the valve 10, the hydraulic connection from the inlet channel 12 to the annular chamber 61 by conditioning the membrane 51 'to the valve seat 26 a is closed. In the open position of the valve 10, the membrane 51 'is lifted from the valve seat 26a and thus the hydraulic connection from the inlet channel 12 to the annular chamber 61 is opened.
  • the operation of the expansion machine 20 is as follows:
  • the shaft seal 25 seals the filled with working fluid valve chamber 11 to the ambient space 40 from.
  • the ambient space 40 may be filled with, for example, air or with transmission oil.
  • the sealing lip 25a of the shaft seal 25 in the direction of the valve chamber 11, so curved towards the expansion machine.
  • This is a typical for an expansion machine 20 arrangement of the sealing lip 25a. That is, in the valve chamber 11, a greater pressure must prevail than in the ambient space 40, in order to press the sealing lip 25a on the output shaft 24 and thus to achieve a sealing effect.
  • the valve 10 is preferably arranged in expansion machines 20, which are operated at least temporarily in negative pressure; that is, the outflow area 22 of these expansion machines 20 has, at least temporarily, a lower pressure than atmospheric pressure.
  • the pressure level of the valve chamber 11 is at the low pressure level of the expansion machine 20, ie at the pressure level of the discharge area 22.
  • the valve space 11 is hydraulically connected or connectable to the discharge area 22, it must be maintained at a pressure level by a device is above the surrounding space 40 to the sealing effect through the shaft seal 25 to receive. And thus the valve chamber 11 must be maintained above the pressure level of the Ausström Anlagens 22, if this falls below the pressure level of the ambient space 40.
  • valve 10 When the valve 10 is open, the hydraulic connection from the valve chamber 11 to the outflow region 22 is opened, the valve chamber 11 will thus assume the pressure level of the outflow region 22. As long as the outflow region 22 has a greater or equal pressure than the surrounding space 40, a sealing effect of the shaft sealing ring 25 is thereby achieved. If the pressure in the outflow region 22 now falls below the pressure of the surrounding space 40, for example because the expansion machine 20 is operated under reduced pressure, then the valve 10 is closed and thus the hydraulic connection from the valve chamber 11 to the outflow region 22.
  • the valve chamber 11 is connected via the throttle 9 hydraulically constantly connected to an area whose pressure level during operation of the expansion machine 20 is above the pressure level of the ambient space 40, for example, with the inflow 21, as in the embodiments of FIGS. 1 and 2 shown.
  • the valve 10 When the valve 10 is closed, the pressure in the valve chamber 11 thus increases to the pressure level of this area.
  • the valve 10 is opened, a pressure gradient arises at the throttle 9.
  • the rigidity of the diaphragm 51, 51 ' has an effect on the opening and closing behavior of the valve 10 in the embodiments of FIGS Figures 3 and 4 .
  • the membrane 51, 51 'designed to be soft for example as an elastomeric membrane or as a thin metallic membrane in order to design the opening and closing behavior of the valve 10 simple and robust over the above-mentioned diameter can.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lift Valve (AREA)
EP15784670.0A 2014-12-23 2015-10-22 Expansionsmaschine mit wellendichtring und ventil Active EP3237729B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014226954.7A DE102014226954B3 (de) 2014-12-23 2014-12-23 Expansionsmaschine mit Wellendichtring und Ventil
PCT/EP2015/074518 WO2016102100A1 (de) 2014-12-23 2015-10-22 Expansionsmaschine mit wellendichtring und ventil

Publications (2)

Publication Number Publication Date
EP3237729A1 EP3237729A1 (de) 2017-11-01
EP3237729B1 true EP3237729B1 (de) 2019-04-24

Family

ID=54347535

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15784670.0A Active EP3237729B1 (de) 2014-12-23 2015-10-22 Expansionsmaschine mit wellendichtring und ventil

Country Status (5)

Country Link
US (1) US10364692B2 (zh)
EP (1) EP3237729B1 (zh)
CN (1) CN107109945A (zh)
DE (1) DE102014226954B3 (zh)
WO (1) WO2016102100A1 (zh)

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2175868A (en) * 1936-10-30 1939-10-10 B F Sturtevant Co Packing
CH329142A (de) * 1953-05-08 1958-04-15 Bosch Gmbh Robert Uberdruckventil
CH550348A (de) * 1972-10-11 1974-06-14 Bbc Brown Boveri & Cie Sperrmedium-labyrinthdichtung.
US4765227A (en) * 1982-05-28 1988-08-23 Teledyne Hyson Die cylinder assembly
US4630642A (en) * 1984-12-03 1986-12-23 Tom Mcguane Industries, Inc. Check valve and water injection systems and fuel systems utilizing the same
GB2393766A (en) * 2002-10-03 2004-04-07 Alstom A sealing arrangement for a turbine
JP2005201366A (ja) * 2004-01-15 2005-07-28 Toyota Industries Corp 軸封装置及び圧縮機
US8622690B1 (en) 2010-12-01 2014-01-07 Florida Turbine Technologies, Inc. Inter-propellant thrust seal
DE102012222010A1 (de) * 2012-11-30 2014-06-05 Robert Bosch Gmbh Expansionsmaschine
CN103746493B (zh) * 2014-01-07 2016-08-17 天津大学 一种应用于orc的高速透平-发电机的主轴密封装置
CN203730202U (zh) 2014-02-28 2014-07-23 南京贝奇尔机械有限公司 Rpt型水轮机主轴密封装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
DE102014226954B3 (de) 2016-06-30
EP3237729A1 (de) 2017-11-01
CN107109945A (zh) 2017-08-29
WO2016102100A1 (de) 2016-06-30
US10364692B2 (en) 2019-07-30
US20180171811A1 (en) 2018-06-21

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