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
  • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
  • F16K15/00—Check valves
  • F16K15/14—Check valves with flexible valve members
  • F16K15/144—Check valves with flexible valve members the closure elements being fixed along all or a part of their periphery
• • 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
  • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
  • F01L1/36—Valve-gear or valve arrangements, e.g. lift-valve gear peculiar to machines or engines of specific type other than four-stroke cycle
• • 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
  • F01L11/00—Valve arrangements in working piston or piston-rod
  • F01L11/02—Valve arrangements in working piston or piston-rod in piston
• • 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
  • F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
  • F01L3/20—Shapes or constructions of valve members, not provided for in preceding subgroups of this group
  • F01L3/205—Reed valves
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
  • F02G2270/00—Constructional features
  • F02G2270/90—Valves

Definitions

• the invention relates to a system comprising an intake or exhaust valve for a gas engine under pressure.
• a pressurized gas engine is an expansion motor where a maximum pressure prevails substantially continuously in an intake duct or motor supply.
• a particular embodiment of such a pressurized gas engine is an Ericsson type hot gas engine.
• US 2005/0257523 discloses an Ericsson type hot gas engine having an intake valve and an exhaust valve both having a circular shaped flat head mounted at the end of a substantially cylindrical rod. The opening and closing of the exhaust and of the intake by these valves is effected by using a camshaft associated with each of the valves, pressing on the end opposite to the flat head of the cylindrical rod. of each of the valves. The camshafts are set in motion from the rotational movement of the crankshaft of the Ericsson engine.
• One of the aims of the invention is to provide an improved system comprising an improved valve for either the intake or the exhaust for a pressurized gas engine that consumes little energy when it is being used. by allowing an optimal circulation of the gas under pressure using the engine.
• a system for a gas engine under pressure comprising: - a variable volume chamber; and a valve comprising a first stationary member for enabling the valve to be attached to the engine, a second movable member for conditionally closing a gas communication passage with the variable volume chamber, first deformable connecting means elastically linking the first and second elements together, the chamber further comprising means for implementing the second movable member of the valve.
• the valve comprises one of the following features: the valve is monobloc; the valve forms a substantially flat blade before deformation; the valve is substantially circular in shape; the first and second elements are in the form of concentric rings; at rest, the first and second elements are substantially in the same plane; at rest, the first and second elements are in two different planes substantially parallel to each other; -
• the valve comprises a third movable member adapted to close a second gas communication passage with the variable volume chamber and second resiliently deformable connecting means connecting the second and third elements together; the third element is substantially planar disc shape; the first and / or second elastically deformable connecting means comprise tabs; the tongues are of substantially spiral shape and uniformly distributed over a circumference of the valve; the implementation means are intended to implement the third movable member of the valve; the implementation means comprise an elastically deformable element mounted on a piston delimiting the variable volume chamber; the elastic deformable element is of the compression spring type.
• a pressurized gas engine comprising at least one
• FIG. 1 is a three-dimensional view of an intake valve according to one embodiment of the invention
• Figure 2a is a sectional view along II-II of the valve of Figure 1 at rest
• Figure 2b is a sectional view along II-II of the valve of Figure 1 in the open position
• - Figures 3a to 3d are simplified schematic sectional views of a pressurized gas engine illustrating the steps of admission of the hot gas under pressure in the variable volume chamber according to the invention
• FIG. 4 is a three-dimensional, half-sectional view of a cylinder of a gas engine under pressure illustrating an exhaust valve according to the invention
• Figure 5 is a three-dimensional top view of the cylinder of Figure 4
• Figure 6 is an exploded partial three-dimensional view illustrating an alternative embodiment of the intake valve and the exhaust valve, both according to the invention.
• the valve (1) is here in the form of a thin blade and a shape of revolution about an axis (X).
• the thickness of the blade is less than or equal to about 1 mm, advantageously less than or equal to 3/10 th of a millimeter.
• valve (1) All the elements forming the valve (1) are made of material from each other, so that the valve is monobloc. Alternatively, the valve is composed of several different materials.
• the first element (3) is said fixed because it allows the attachment of the valve (1) on the gas engine under pressure on which it is intended to be mounted.
• the second element (5) is said to be mobile and is connected to the first element by the first series of tongues (9).
• the tongues (9) are of substantially spiral shape and wrap around the axis (X) of the valve (1).
• the tabs (9) are uniformly distributed over an outer circumference of the second movable member
• the tongues (9) are derived from materials of the movable element (5) and the fixed element
• the cutouts (11) thus produced have, themselves, a spiral shape, wrapping around the axis (X) of the valve (1).
• Each of the spiral cuts (11) has, in a clockwise direction, a first outer end (120) which is located at an inner circumference of the first fixed member (3), followed by a winding around and to the axis (X) of the valve (1) to terminate at a second end (121), which is substantially on an outer circumference of the second movable member
• each cut (11) delimits, in a first half approximately, an outer edge of a first tongue (9) and, in a second half about, an inner edge of a second tongue (9) successive to the first tongue (9).
• a flare (91) and (92) forming the ends of the tongues (9).
• the third element (7) which is also mobile, is connected to the second movable element (5) by the second set of tongues (13) which came from both the third element mobile (7) and the second movable element (5).
• the series of tabs which came from both the third element mobile (7) and the second movable element (5).
• (13) are at a number of three, uniformly distributed over an outer circumference of the third movable member (7) and an inner circumference of the second movable member (5), and are made from a series of spiral cuts (15) around and towards the axis (X) made in the blade forming the valve
• the valve (1) is substantially flat as shown in Figure 2a.
• the second series of tongues 13 is initially deformed, then the first series of tongues (9) is deformed, so the valve has in section the shape illustrated in Figure 2b, the third movable element (7 ), the second movable element (5) and the first fixed element (3) being each in a plane, the three planes being substantially parallel to each other and perpendicular substantially to the axis (X) of the valve (1).
• the pressurized gas engine (20) has a piston (21) connected by a link (23) to a camshaft (24).
• the piston (21) is slidable along an axis, here vertical in the figures, in a cylinder (22) closed on the top by a yoke plate (27).
• the piston (21) has on an upper face a compression spring (26), here a coil spring.
• the motor (20) has above the yoke plate (27) a compression chamber (25) adapted to contain, during operation of the engine (20), a hot gas under pressure.
• the yoke plate (27) has a first communicating passage (28) formed of a series of openings between the pressure chamber (25) and the cylinder (22) and a second communicating passage (29).
• the second communicating passage (29) is formed of a substantially cylindrical opening of cylindrical shape and is opposite the compression spring (26). It is able to receive a free end of this compression spring (26) during operation of the gas engine under pressure (20).
• the valve (1) according to the invention is mounted on a face of the yoke plate (27) delimiting the compression chamber (25). In the rest position, as illustrated in FIG.
• the second movable element (3) closes the first communicating passage (28) while the second movable element (7) closes the second communicating passage (29), the first element fixed (3) being fixed by means known per se on the plate forming cylinder head (27) or crimped in vertical walls delimiting the compression chamber (25).
• This deformation of the compression spring (26) is made possible because the existing pressure in the compression chamber (25) applies the inlet valve (1) against the yoke plate (27).
• the force generated by this pressure on the third movable element (7) (this force has a value equal to the pressure multiplied by the surface of the third movable element (7)) is greater than the opposite force exerted by the compression spring (26) during its compression.
• the force exerted by the latter on the third movable element (7) becomes greater than the force exerted by the pressure in the compression chamber (25) on the same third element mobile (7). Then, the compression spring (26) lifts the third movable member
• the compression spring (26) As the piston continues its downward movement, the compression spring (26) is in a relaxed rest position. Therefore, the free end of the spring (26) in contact with the third movable member (7) follows the movement of the piston and back down into the second communicating passage (28) under the biasing forces due to the deformed tongues (13), on the one hand, and (9) on the other hand.
• the second (5) and third (7) movable elements of the valve (1) perform the same movement and are successively plated and respectively on the first communicating passage (28) and the second communicating passage (29), closing the latter. Therefore, no flow (G) of hot gas under pressure exists between the compression chamber (25) and the variable volume chamber.
• variable volume chamber (30) expands and the piston (21) continues its descent until reaching a bottom dead point which will trigger the start of the exhaust phase described below. .
• valve (1) Once the valve (1) has closed the communicating passages (28) and (29), the latter remains pressed in the closed position under the effect of the pressure difference that exists between the pressure prevailing in the compression chamber ( 25) and the lower pressure prevailing in the variable volume chamber (30).
• the only amount of energy required to move the intake valve (1) is the energy required to deform the compression spring (26) to contiguous turns. It should be noted that this energy necessary to deform up to contiguous turns the compression spring (26) is very low compared to the energy required to implement camshafts coming to press valves as in the US document 2005/0257523.
• the exhaust valve (40) is, in principle, similar to the intake valve (1) which has just been described.
• the exhaust valve (40) is generally substantially of revolution and is in the form of a thin blade.
• the thickness of the blade is less than or equal to about 1 mm, advantageously less than or equal to 3/10 th of a millimeter.
• the exhaust valve (40) has a first fixed element (42) whose role is similar to the first fixed element (3) of the inlet valve (1) described above.
• the exhaust valve (40) has a second movable member (41) whose role is similar to the second movable member (5) of the intake valve (1).
• a series of tabs (43) connects the first movable member (42) to the second movable member (41).
• the embodiment of the tabs (43) is similar to that of the tabs (15) and (9) that we have described for the intake valve (1).
• the noticeable difference between the intake valve (1) and the intake valve (40) is that at rest the exhaust valve is in the open position as shown in FIG. 4, i.e. that the second element
• the yoke plate (27) has a series of orifices (44) forming a communicating passage between the variable volume chamber (30) and the exhaust duct (50). These openings (44) are uniformly distributed over a circumference and are opposite the movable member (41) of the exhaust valve (40). It should be noted that the orifices (28) forming the first communicating intake passage are themselves uniformly distributed over a circumference and facing the second movable element (5) of the intake valve as shown in FIG. 5).
• the piston (21) is equipped with a support spring (45) whose constitution here is similar to that of the exhaust valve (40). Indeed, the support spring (45) has a first fixed element (47) adapted to allow the attachment of the support spring
• the second movable element (46) of the support spring (45) is connected to the first fixed element (47) of the support spring (45) by a series of spiral tongues (48) similar to the spiral tongues (43) of the exhaust valve (40).
• the pressure in the variable volume chamber (30) is greater than the existing pressure in the exhaust duct (50) to which the orifices (44) provide access.
• This pressure difference makes it possible to keep the second movable element (41) pressed onto the yoke plate 27 closing the orifices (44) in the closed position, in spite of the return forces. exerted by the tabs (43) then elastically deformed.
• This orifice (52) is connected to a pipe (51) which leads, in its upper part, to the exhaust duct.
• the tubing (51) establishes a so-called load shedding circuit. Therefore, thanks to this unloading circuit, the pressure in the variable volume chamber (30) becomes equal to the pressure in the exhaust pipe, beyond the openings (44).
• the second movable element (41) of the exhaust valve (40) is "peeled off” from the yoke plate (27) thus opening the openings (44) that will evacuate the gas contained in the variable volume chamber (30) during an ascent to the top dead center of the piston (21).
• variable volume chamber during an intake phase may fluctuate around an ideal rate that avoids halting the fuel cycle. engine operation.
• the use of an exhaust valve according to the invention makes it possible to "erase” and to overcome these possible fluctuations:
• the opening of the exhaust valve according to the invention occurs before the bottom dead center of the piston. This avoids generating, at the end of the stroke of the expansion cycle, a vacuum in the variable volume chamber opposite the movement of the piston and therefore energy consuming. •
• the unloading circuit allows an opening of the exhaust valve according to the invention in the bottom dead center position of the piston which avoids halting the operation of the cycle.
• the inlet valve (100) of this embodiment differs from the inlet valve (1) previously described by the presence of a series of orifices (101) uniformly distributed over a circumference of the second movable member of the intake valve (100). Between two successive orifices (101), the second movable element of the intake valve
• the number of orifices (101) is identical to the number of orifices forming the first communicating passage (28) in the yoke plate (27). However, each orifice of the yoke plate (27) faces an arm (102) of the second movable member of the intake valve (100). Thus, when the second movable member of the intake valve (100) is pressed against the yoke plate (27), each arm (102) closes a corresponding orifice of the first communicating passage
• the exhaust valve (110) of this embodiment differs from the exhaust valve (40) previously described by the presence of a series of apertures (111) uniformly distributed over a circumference second movable member of the exhaust valve (40).
• an arm of material (112) is located between two orifices (111) consecutive.
• the number of ports (111) is similar to the number of exhaust ports (44) provided in the cylinder head plate (27). However, each arm
• valves according to the invention reconciles low energy expenditure to their implementation and optimization of gas flows. It is thus possible to achieve high engine speeds with a high efficiency of operation.
• the difference in engine power involved in a conventional combustion engine and a gas engine under pressure may be a factor of ten. This factor exists between an explosion generating about 30 bars (in a combustion engine) and the expansion of compressed gas at 3 bars (in a gas engine under pressure). Since the pull of a loosely compressed gas is lower, the passive resistances related to friction, camshaft drive and the activation force of the valve springs rapidly take on significant proportions which can destroy the overall yield.
• the distribution mechanism using valves according to the invention sets in motion small masses (the blade forming the valves according to the invention has a thickness less than or equal to 1 mm, advantageously less than or equal to 3 / 10th of a mm) retained by elastically deformable connecting means having low activation forces.
• the reduction of moving masses allows response times compatible with high stress frequencies without oversizing the elastically deformable connecting means stiffness.
• the maximum pressure prevails continuously in the supply duct.
• the effort required to open a traditional intake valve is proportional to its surface.
• the stepped opening of the intake valve according to the invention decreases the necessary activation energy while providing a large pressure gas flow from the compression chamber to the variable volume chamber. This helps to power the motor optimally by improving the filling rate at high speed.
• the activation energy of a monolithic equivalent unstaged valve would be ten to thirty times greater. Thus, it makes it possible to increase the passage section of the gas independently of the force required to open the valve according to the invention. Which is impossible with a traditional valve.
• valves according to the invention in a pressurized gas engine makes it possible to obtain high expansion efficiencies by minimizing the energies of activation of the distribution while being compatible with large gas flows facilitating the rise in temperature. engine speed without destroying the fill rate of the variable volume chamber.
• the valves according to the invention work naturally in the direction of the gas flow: it is the difference in pressure between the two faces of the valve which conditions its opening or closing.
• the valves according to the invention which then operate against the flow of gas and therefore against the pressure difference between the two faces of the valve.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Physics & Mathematics (AREA)
• Geometry (AREA)
• Valve Device For Special Equipments (AREA)

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• 2007
  • 2007-09-06 FR FR0757397A patent/FR2920854B1/fr not_active Expired - Fee Related
• 2008
  • 2008-09-05 CA CA2698499A patent/CA2698499A1/fr not_active Abandoned
  • 2008-09-05 US US12/676,573 patent/US20100186720A1/en not_active Abandoned
  • 2008-09-05 EP EP08803777A patent/EP2185845A1/de not_active Withdrawn
  • 2008-09-05 WO PCT/EP2008/061808 patent/WO2009030761A1/fr active Application Filing

Non-Patent Citations (1)

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