Classifications

• • 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
  • F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
  • F01B25/00—Regulating, controlling or safety means
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
  • F01B29/00—Machines or engines with pertinent characteristics other than those provided for in preceding main groups
  • F01B29/08—Reciprocating-piston machines or engines not otherwise provided for
  • F01B29/10—Engines
  • F01B29/12—Steam engines
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
  • F01L25/00—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means
  • F01L25/08—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by electric or magnetic means

Definitions

• the invention relates to a high-pressure steam engine according to the preamble of claim 1.
• the disadvantages of the electric drive are: The low capacity of the battery, the high power to weight ratio caused by the battery and the long charging time of the battery.
• Ne 7 m - m NT.
• the efficiency of a steam engine can be easiest compared to the quality level ⁇ i using the h, s table, which can be compared and determined in a lossless, heat-tight machine without harmful space and without throttling.
• the difference h £ -h is therefore, apart from the mechanical losses, the calorific value of all losses occurring in the real machine listed below: a) Heat exchange with the cylinder walls (wall loss). b) Flow losses in the control elements (throttle losses). c) Losses that arise when operating with slightly overheated or saturated steam (inlet condensation). d) loss due to incomplete stretching. This loss increases the more the economic filling is exceeded. e) Loss in the case of small fillings in which the counter pressure line is exceeded due to the expansion. With this loss, the thermal energy of the back pressure steam flowing back into the cylinder must be returned to the working process through the compression work. Due to the deeper expansion, the cylinder wall temperature is lowered and the heat exchange loss is increased.
• inlet valves Inlet valves, overflow valves and outlet valves cause flow and throttle losses.
• Flow losses are caused by the free-standing evaporator and the pipeline leading to the first cylinder.
• the pumping work when inserting the steam into the back pressure condenser is not adiabatic and reversible, but an energy loss.
• pressure drops When the steam passes from the HP to the LP cylinder, pressure drops occur. Further losses occur on glands (to the outside) and on control units.
• This device has only an auxiliary function for the main control device of a steam engine.
• the electrical relay affects only part of the main control member, which is movable against the part affected by the machine. With this device, no steam engine can be set by control commands from the driver, from standstill to start-up and to different speeds.
• the relays m and m 1 switching magnets are only switched on for a partial or complete closing of the main or auxiliary valve FIG. 5.
• the invention has for its object to provide a steam engine operated with supercritical pressure and temperature, with which a high thermal efficiency and a high mechanical efficiency can be achieved.
• Fig. 1 a cylinder 4, the high pressure steam engine in
• Section which is enclosed by a supply air jacket space 15, which is guided over the cylinder cover 173, and in a constriction encloses the valve guide shaft 166 and leads to the heat exchanger 231.
• the supply air jacket space 15 is enclosed by a combustion chamber 228. This is connected to the supply air jacket space 15 via a compressor 230.
• the burner nozzles 298 and the evaporator 2 with the superheater 3 are arranged in the combustion chamber 228.
• the combustion chamber 228 is closed by a backflow valve 229.
• the exhaust gas path leads via the damming valve 229 to the heat exchanger 231 and via outlet pipes which lead to the inlet pipes of the supply air jacket space 15 at right angles to the outside.
• valve lift limiting gear 226 in connection with a control magnet 9, which is connected to the steam inlet valve 5 via a valve opening lever 163.
• FIG. 3 A cylinder outlet slot control gear 316, which is connected to the valve lift limiting gear 226 and via a sliding roller 99 and via a transmission lever 22, with the cylinder outlet slot control valve 285 and via the transmission lever 227 with the indicator switch 318, which is connected by a pipe 221 to a Superheater 3 is connected.
• Fig. 5 is a plan view of a cylinder 4, with a
• Valve housing 333 with valve lever shaft seal 54, superheater 3, evaporator 2, supply air jacket space 15, combustion chamber 228, the heat exchanger 231 with
• Fig. 6 shows the engine block 12 with the cylinder 4 in a plan view.
• Fig. 12-13 the piston cooling and lubrication device.
• Fig. 14 a counter vapor brake exhaust valve 199.
• Fig. 16 a crankshaft and connecting rod bearing with roller bearings.
• Fig. 17-18 two twin cylinders that are offset from each other by 45 degrees on a crankshaft.
• Fig. 19-22 a feed water pump 1 with outside adjustment center 197 and inside adjustment cam for a feed water control.
• Fig. 23-26 a piston pressure regulator 148 in connection with the feed water pump 1.
• Fig. 27-33 a collector control device, in connection with the steam engine.
• Fig.41-42 a starting gear 306, for starting the
• Fig. 43-46 a counter-steam braking device, which can automatically set a counter-steam braking when driving downhill by setting the control device for giving steam before TDC.
• Fig. 47-53 a heat accumulator 334, which is connected via rotary slide switch to the forced flow evaporator 2 and to the feed water pump 1.
• the motor When the motor starts up after the working fluid has been brought to a maximum temperature and pressure level by heating, and the water plug, which had formed when the motor is cold, has been pushed out, the motor can be started by a control command from the driver.
• the control magnet 9 is opened for a steam inlet into the cylinder 4 by a suitable electromagnetic control device (collector or Hall control device).
• the steam inlet valve 5, which is held by the closing spring 157 via a closing fork 164 via the valve driver 166 on the valve seat 162, is driven by the armature 167 of the control magnet 9 by the weak spring 211 via the opening lever 163 and the opening fork of the opening lever 163 with the Valve driver 166 is held in a backlash-free contact against the pressure of the
• the steam inlet valve 5 is controlled by the valve lift limiting gear 226 for different valve lift settings. With a small amount of steam, the sliding wedge 301 is pulled against the armature tappet 167 for a small valve lift. For a large valve stroke, it is moved in the other direction to increase the stroke gap between the sliding wedge and the armature tappet.
• the control is carried out by the driving foot lever via the control linkage 300 and the toothed racks 312u.313.
• the cylinder outlet slot control gear 316 can be set to the required ratio. In the event of pressure fluctuations in the evaporator, these are transferred from the indicator switch 218 to the cylinder outlet slot control gear 316 and the gear is adjusted for the gear ratio after the fluctuations via toothed racks and pinions and via the sliding roller 99, by means of which the residual vapor can be compressed to the evaporator pressure .
• the lubrication option with glycol-enriched feed water that is cooled in a cooling circuit.
• An electromagnetic control device that enables high-speed running.
• An environmentally friendly company By heating the evaporator with external, continuous combustion, a complete combustion is achieved which, as the combustion product, delivers harmless carbon dioxide CQz and water.

Landscapes

• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Engine Equipment That Uses Special Cycles (AREA)
• Polarising Elements (AREA)

Applications Claiming Priority (3)

Publications (2)

Family

ID=7831585

Family Applications (1)

Country Status (5)

Families Citing this family (5)

Family Cites Families (9)

• 1997
  • 1997-06-06 DE DE19723748A patent/DE19723748A1/de not_active Withdrawn
• 1998
  • 1998-06-08 DE DE19880764T patent/DE19880764D2/de not_active Expired - Fee Related
  • 1998-06-08 AU AU84330/98A patent/AU8433098A/en not_active Abandoned
  • 1998-06-08 AT AT98934864T patent/ATE201917T1/de not_active IP Right Cessation
  • 1998-06-08 EP EP98934864A patent/EP0920573B1/fr not_active Expired - Lifetime
  • 1998-06-08 WO PCT/DE1998/001541 patent/WO1998055734A1/fr not_active Ceased
  • 1998-06-08 DE DE59800819T patent/DE59800819D1/de not_active Expired - Fee Related

Non-Patent Citations (1)

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