MXPA96004235A - Fluid bearing with flexible linking paracentrar body reciprocan - Google Patents

Abstract

The present invention relates to an improved mechanical transducer having a housing that includes a chamber defined by at least one wall and having a geometric axis of symmetry, the chamber contains a coupling body, which effects a reciprocating movement substantially axially , and is connected to the housing by means of a linkage comprising, at least, a linkage component that includes a flexible spring that applies an axial force on the body, the transducer has an antifriction bearing to minimize the contact between the wall of the chamber and body, wherein the improvement comprises that: a) the bearing is a fluid bearing for applying lateral centering forces on the body, and b) the linkage includes a component that has sufficient lateral flexibility so that the forces of centering exerted by the fluid bearing are at least equal to the sum of all other lateral forces and jercidas on the body, including the lateral force exerted on the body by the linkage, during the normal operation of the transduc

Description

FLUID BEARING WITH FLEXIBLE LINKING TO CENTER RECIPROCATING BODIES FIELD OF THE INVENTION This invention is generally related to thermomechanical or electromechanical transducers of the type in which one or more oscillating bodies mounted on springs that effect a reciprocating or reciprocating movement along an axis of geometric symmetry and which is particularly advantageous for use in free-piston Stirling engines with linear alternators, free-piston Stirling coolers with linear motors, free-cylinder water pumps and free-piston compressors with linear motors.

ANTBCBDKNTKS DK THE INVENTION The misalignment of parts in the thermomechanical and electromechanical transducers that have one or more oscillating bodies mounted on springs, cause these bodies to perform a reciprocating or reciprocating movement along an axis different from the axis of geometric symmetry. The real axis of the reciprocating movement may be parallel, but it is generally not parallel to the geometric axis. These misalignments originate routinely during the manufacture and assembly of P1253 / 96MX mechanical parts, because the dimensions, angularity and planarity can not be carried out perfectly. In practice, machine designers define tolerances (ie tolerable deviations from perfection) in dimensions, angularity and planarity and, when these imperfect parts are assembled, they result in misalignments. These misalignments can completely eliminate the physical gap between a reciprocating body and its cylinder. The resulting mechanical contact causes friction, wear and, in extreme cases, the engarrotamiento of the reciprocating body in its cylinder. This mechanical contact can be lubricated by contact bearings, but the dissipation of the associated frictional energy degrades the efficiency of the transducer and the associated mechanical wear reduces its required maintenance interval or service life. In electromagnetic and electromechanical transducers (such as those described in U.S. Patent Nos. 4,346,318; 4,349,757; 4,545,426; 4,602,174; and 4,623,808), misalignment of the transducer reciprocating body introduces a radial magnetic force that increases misalignment and therefore, the force until the reciprocating and stationary parts are strongly attracted towards an undesirable mechanical contact.

P1253 / 96MX In thermomechanical transducers (such as those described in US Patents Nos. 3,788,778; 3,937,600; 3,947,155; 4,036,108; 4,179,630; 4,353,220; 4,538,964; 4,545,738; 4,644,851; 4,649,283; 4,721,440p; 4,336,757; 4,862,695; and 5,255,522) , which have a sealed gap between the reciprocating body and its cylinder, any eccentricity due to misalignment reduces the resistance of the fluid to flow through the sealed gap. If the reciprocating body is a piston, the increased flow of fluid through the sealed gap reduces the compression ratio achieved by the piston. If the reciprocating body is a displacement device that pushes the fluid through a system of heat exchangers, the increased flow of fluid through the sealed gap reduces the effectiveness of the intended heat transfer process. Gas bearings (such as those described by JW Powell in Design of Aerostatic Bearings and in other works and, in US Patents Nos. 2,876,799, 2,907,304, 3,127,955, 4,545,738, and 4,644,851, are desirable in thermomechanical transducers and electromagnets that have one or more oscillating bodies mounted on springs and in which energy efficiency and long service life are important, because they eliminate mechanical contact, friction and P1253 / 96MX wear between the working surfaces of the reciprocating bodies and their cylinders. Practical gas bearings can not generate large radial forces to re-establish a discouraged reciprocating axis of reciprocating body, acceptably close to the geometrical axis of symmetry in these transducers, however, without dissipating an excessive amount of energy, thereby degrading the energy efficiency of the transducer. The present invention reduces the amount of radial force that the gas bearings must exert and, therefore, the amount of energy that they must dissipate during the operation to re-establish or restore a reciprocating axis, misaligned from a reciprocating body, acceptably close to the axis geometric symmetry in these transducers.

BRIEF DESCRIPTION OF THE INVENTION The present invention is an improved mechanical transducer having an oscillating body that effects a reciprocating or reciprocating movement, within a cylinder, along, specifically, a geometric axis of symmetry with an axially flexible spring, an axially rigid and radially flexible member and a fluid bearing. The present invention differs from the prior art devices in that it selectively interposes the axially rigid member and radially P1253 / 96MX flexible among other mechanical parts, to reduce the amount of radial force, that the fluid bearing must exert on the reciprocating body, to stabilize its real reciprocating axis acceptably close to the geometric axis of transducer symmetry, thereby avoiding the undesirable mechanical contact between the reciprocating body and its cylinder, as well as an undesirable reduction in the resistance to the flow of the fluid through the seal of the reciprocating body.

BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a simplified schematic drawing in axial section illustrating how one of the many types of misalignment may cause a reciprocating or reciprocating motion along a shaft to be oscillated, mounted on springs. different from the geometric axis of symmetry. Figure 2 is a schematic diagram in axial section illustrating, in its most simplified form, the basic principle of operation of the embodiments of the invention. Figures 3A and 3B show plan and edge views of a flat spring which is the preferred axially flexible member of the invention. Figures 4A, 4B and 4C are diagrammatic views P1253 / 96MX _ axial illustrating two components of lateral flexibility in the axially rigid and laterally flexible member of the invention. Figure 5 is a schematic and axial section diagram of one embodiment of the invention of the type illustrated in Figure 2. Figure 6 is a schematic diagram in axial section of the preferred embodiment of the invention of the type illustrated in Figure 2. Figure 7 is a schematic diagram in axial section of an alternative embodiment of the invention of the type illustrated in Figure 2. Figure 8 is a schematic diagram in axial section of another alternative embodiment of the invention of the type illustrated in Figure 2. Figure 9 is a schematic diagram in axial section of another alternative embodiment of the invention of the type illustrated in Figure 2. Figure 10 is a schematic diagram in axial section of another alternative embodiment of the invention of the type illustrated in Figure 2. FIGS. HA and 11B illustrate, in axial section, two embodiments of a gas spring that can also be used as the axially flexible member of the invention.

P1253 / 96MX Figure 12 illustrates, in axial section, a magnetic spring that can also be used as the axially flexible member of the invention, Figure 13 illustrates, in an oblique perspective view, a special type of flat spring that can be used as the axially flexible member and also as the radially flexible member of the invention. In describing the preferred embodiments of the invention illustrated in the drawings, for the benefit of better clarity, specific terminology was used. However, it is not intended that the invention be limited to the specific terms selected in this manner and it will be understood that each specific term includes all technical equivalents that function in a similar manner to achieve a similar purpose. In particular, the cross section through the geometric axis of transducer symmetry that shows a cylinder and its reciprocating coupling body, can be a triangle, square, pentagon, hexagon and any other regular or irregular polygon or it can be circular, elliptical or any other curve closed.

DETAILED DESCRIPTION PE THE PREFERRED MODALITIES It is useful to review some terminology used by those experienced in the technique and used in P12S3 / 96MX relation to the following description of the invention. Each time it is used in the present, the term mechanical transducers refers to all types of reciprocating transducers that interconvert mechanical energy in other types of energy. Specifically, but not exclusively, thermomechanical transducers are included in the form of free-piston Stirling engines that convert high-temperature thermal energy into mechanical energy, and thermodynamic transducers in the form of free-piston Stirling chillers that perform mechanical work to absorb energy. thermal at low temperature and that they expel it at a hotter temperature. Also specifically included are linear comprrs that perform mechanical work to raise the prre of a gas or to transport a fluid. The electromechanical, electromechanical, electromechanical transducers in the form of linear electric alternators, which convert mechanical energy into electrical energy and linear electric motors that convert electrical energy into mechanical energy are also specifically included. In these mechanical transducers, an axially flexible spring is used to substantially resonate the reciprocating mass in order to increase the efficiency with which the energy is interconverted. In some cases, mass-spring relationships do not P12E.3 / 96MX are exactly resonant due to other practical considerations such as, for example, the desire to maximize the energy transfer, but, all cases are substantially within the so-called resonant peak of the response to the transducer frequency mechanic. Thus, the power factor in a mechanical transducer outside of resonance is not exactly 1.0, but is usually greater than 0.5. Axially flexible springs commonly used include mechanical springs such as helical coil, gas springs, and electromagnetic springs. In these mechanical transducers, the term flexibility refers to the amount of deflection a mechanical part undergoes as it changes shape in response to an applied force. The term rigidity refers to the inverse of the flexibility, that is, the amount of force required to flex or deform a mechanical part at a particular distance. Thus, a flexible member is a mechanical part that flexes or deforms over a relatively large distance compared to the distance that a rigid member is flexed or deformed by an applied force. Additionally, a mechanical part can be shaped so that it is flexible, in its response to forces applied to a direction, and rigid, in its response to forces P1253 / 96MX applied in another direction. For example, a thin solid rod firmly attached to an immovable object at one end comprs axially much lthan it bends laterally when a particular force is applied in those directions. Thus, it can be said that a thin rod is axially rigid and laterally flexible. In the past, helical springs have been used in these mechanical transducers to substantially resonate the reciprocating mass, but the compron of a helical spring is accompanied by an inclination of its longitudinal axis at an angle with respect to the longitudinal axis through the relaxed spring . When a laterally constrained helical spring is comprd, it exerts a lateral force against that restriction and this lateral force is proportional to the axial stiffnof the spring. When the lateral restriction is the cylinder inside which a piston, connected to the spring, makes a reciprocating movement, that lateral force prs the piston against the wall of the cylinder causing friction and wear. Any fluid bearing that tries to avoid this friction and wear must overcome that lateral force by dissipating the energy proportionally to the force, as it is presented. For design reasons, as the reciprocal frequency of a P12S3 / 96MX piston of a given mass, the axial stiffness of the required spring, the associated lateral force and the energy dissipation of the fluid bearing increase with the square of the frequency. Theoretically, the interposition of a radially flexible member between a coil spring and a piston or between a coil spring and a housing connected to the cylinder, reduces the amount of force, which the fluid bearing must apply, to the amount required to arch the member. radially flexible. However, in practice, the degree of arching in a flexible member, used with a single helical spring, is so great that the danger of warping the flexible member, which is also under an axial compressive load of associated hydrostatic and inertial forces With the reciprocating movement of the piston, it is unacceptably large. When the lateral restriction in a helical spring is a rigid mechanical connection with other helical springs symmetrically spaced about a common symmetry axis parallel to the geometric axes of symmetry of the individual springs, then there is a rotational orientation of the individual springs, such that its lateral forces tend to cancel out, so that the lateral displacement of the group of springs as a whole and the lateral force, P1253 / 96MX necessary to arch or bend a radially flexible member to undergo this displacement, are so small that the risk of warping of the radially flexible member is also small. In practice, the oscillating body mounted on the spring of a mechanical transducer performs a reciprocating movement along an axis different from the geometric axis of transducer symmetry for two reasons: 1) the gravitational weight of the reciprocating body and 2) the misalignments within the suspension system of the reciprocating body. Normally, the gravitational displacement of the reciprocating shaft can be overcome by fluid bearings with little energy dissipation. The present invention specifically reduces the influence of mechanical misalignment on the reciprocating axis. The amount of force that the fluid bearings must exert to overcome these misalignments is directly related to the radial stiffness of the entire structure that suspends the reciprocating body within its cylinder. In the present invention, the axially rigid and radially flexible member within the suspension system controllably reduces this stiffness to that of the radially flexible member. Figure 1 illustrates in axial cross section how a misalignment (exaggerated for clarity) P1253 / 96MX can cause an oscillating body mounted on springs to reciprocate along an axis 1 remote from or separated from the geometric axis of symmetry 2 of a thermomechanical, electromagnetic or electromechanical transducer. In Figure 1, the oscillating body is a piston 4 and the width of the gap between the piston 4 and its surrounding cylinder 3, formed in a housing, has been exaggerated for reasons of clarity. A piston, by definition, is a reciprocating body with a difference in pressure axially therethrough. In mechanical transducers in which the invention described herein may be applied, the reciprocating body may also be a displacement device, which, by definition, is a reciprocating body with a temperature difference, axially therethrough. The reciprocating body can also be a magnet blade, a moving coil or a moving magnet of an alternator or linear motor. The right angle at one end of the cylinder 3 in Figure 1 is manufactured imperfectly since its end deviates from a plane at a right angle to the geometric axis of symmetry 2. The piston 4 is suspended from a flat spring 6 within of a chamber formed as the cylinder 3 by means of a rod 5, axially and radially rigid, which resonates the reciprocating mass of all P1253 / 96MX these parts and that is rigidly attached to the end of cylinder 3, manufactured imperfectly. As a result, the actual reciprocating axis 1 is deviated or offset from the geometric axis of symmetry 2 and a large radial force would have to be exerted against the piston 4 to restore its reciprocating axis 1 acceptably close to its axis of symmetry. Figure 2 illustrates, in axial section, the basic principle of operation of the embodiments of the invention in its most simplified form. As in Figure 1, the right angle at one end of the cylinder 13 is manufactured imperfectly, since its end deviates from the right angle of its geometric axis of symmetry. However, in this case, an axially rigid and radially flexible rod 15 is interposed between the piston 14 and the flat spring 16. As a result, the small force exerted against the piston 14 by the fluid flowing from the cavities 17, 18, 19 and 20 of the fluid bearing towards the gap between the piston 14 and the cylinder 1,3 during the operation of the transducer, is capable of restoring the reciprocating axis 11 of the piston 14 in an acceptable manner towards the geometric axis of symmetry 12. Figure 3A and Figure 3B show a plan view and a side view, respectively, of a dock P1.253 / 96MX flat. A flat spring consists of a multiplicity of beams or arms in a plane, which stores mechanical energy as the beams or arms undergo a common deflection, perpendicular to the plane. The flat spring shown in Figure 3A has four of these beams or arms. The flat spring of Figure 3 has a diameter of approximately 134 mm and a thickness of approximately 2 mm and is constructed from one of the following carbon steels AISI, 1035, 1045, 1055, 1075, 4140 or 4130. Figure 4 shows an axially rigid and laterally flexible solid rod for which, lateral flexibility is then analyzed. Other cases could be analyzed with reference to standard mechanical engineering texts such as Roark's Formulas for Stress and Strain The lateral flexibility CL of the rod shown in Figure 4A has two components, the translational shown in Figure 4B and the angular shown in Figure 4C, the translational component Cy of the flexibility refers to the translational displacement and the free end of the rod, while the angular component C de of the flexibility refers to the angular displacement del of the free end: O, = Cy + CT The translational component Cy of radial flexibility is: P1253 / 96MX Cy = y / W = L3 / 3EI W = a lateral force, E = Young's modulus of the rod material, and I = the moment of inertia of the rod. In the case of a rod or radius R, I = pR4 / 4 The angular component CT of lateral flexibility is: C? = T / = L / 4EI where? = angular displacement of the free end of the rod, L = length of the rod, and M = the applied moment, that is, the pair of forces acting along parallel lines separated in opposite directions. To minimize the dissipation of energy from a gas bearing in a mechanical transducer, the lateral flexibility of the rod is designed to be the maximum possible without bending damage of the rod under the applied axial force F, which arises from thermodynamics and inertia in mechanical transducers, such as those that are the subject of the present invention. The bending load Fb of a solid rod is: Pi; 53 / 96MX Fb = p2 EI / 4L2 To identify the conditions of a desired high lateral flexibility for a particular warping load, the proportion of each component of lateral flexibility with respect to the warping load is examined in the separated. The substitution of the previous equations produces the following expressions for these proportions: Cy / Fb = (64 / 3p2). (L5 / R8) '(l / E2) C? / Fb = (16 / p2). (L3 / R8Ml / E2) By inspection, the high flexibilities desired per unit of sag resistance are obtained by manufacturing long narrow rods of materials with small Young modules. The merit values Fy and FT with units of Pa ~ 2 (Pa = Passes) for a given design can be defined as; The derivations for the merit values of laterally flexible and rigid stainless steel and aluminum rods, respectively, for a particular linear compressor are shown in the following table: P1253 / 96MX L R E F and FT (cm) (mm) (x 1011 Pa) (Pa "2) (Pa" 2) Flexible 6.0 1.5 0.7 '10"14 10 ~ 18 Rigid 2.0 3.0 2.4 10"18 10" 23 In practice, an engineer would leave a factor of safety in the design of the rod to make it strong enough to support a warping load Fb, say 3 times the applied axial force F. Next, the engineer would select the length, radius and material of the rod to maximize the merit values within any of the limits that may be imposed by other design constraints. Figure 5 illustrates, in axial section, a practical embodiment of the invention in which an electromagnetic, electromechanical treinsductor has an oscillating magnet blade mounted on springs which effects a reciprocating movement within a radially adjacent cylinder. In this mode, the mechanical transducer is an electromagnetic, electromechanical transducer that functions as a linear permanent magnet motor. The reciprocating body of the transducer is the magnet blade 131 carrying the permanent magnets 132 of the linear motor. The magnet blade 131 effects a reciprocating movement with respect to the radially adjacent cylinder P1253 / 96MX 133. The pressurized fluid from an external source enters the pressure chamber 134 through a unidirectional valve 135 and exits towards the space between the magnet blade 131 and the cylinder 133 through the conduits 136, 137, 138 and 139 and provides a fluid bearing. The magnets 132 of the linear motor that effect a reciprocating movement with respect to an internal magnetic flux loop member 140 and to an external magnetic flux loop member 41 [sic], comprised of a material of high permeability, which together constitute a trajectory of magnetic flux with spaces 142 and 143 around an armature coil 144 of electrically conductive wire, the magnet vane 131 is connected to the planar spring 147 by means of a rigid transverse member 145 and an axially rigid and radially flexible solid rod 146 The flat spring 147 is connected to a rigid housing 148 which is rigidly connected to the cylinder 133. The radially flexible member 146 reduces the radial force that the fluid flowing from the fluid bearing conduits 136, 137, 138 and 39. must generate to restore the reciprocating axis acceptably near the geometric axis of symmetry 149. Figure 6 illustrates, in section axial cross section, the preferred embodiment of the invention in P12 £ 3 / 96MX which a thermomechanical transducer is mechanically connected to an electromagnetic, electromechanical transducer, both have oscillating bodies mounted on springs that effect a reciprocating movement with respect to. a radially adjacent cylinder. In this mode, the thermomechanical transducer is a free piston compressor and the electromechanical electromagnetic transducer is a permanent magnet linear motor. The reciprocating body of the compressor is a hollow piston 31 which effects a reciprocating movement with respect to a radially adjacent cylinder 32. The interior of the piston 31 serves as a source of pressurized fluid for a fluid bearing. The fluid enters the piston 31 from the compression space 33, through which the unidirectional valve 34 exits towards the separation opening between the piston 31 and the cylinder 32, through the conduits 35, 36, 37, and 38. The reciprocating body of the linear motor is its magnet blade 39 which effect reciprocating movement with respect to its inner magnetic flux loop member 40 and its outer magnetic flux loop member 41, which together constitute a magnetic flux path with two spaces 42 and 43 around an armature coil 44 of electrically conductive wire. The two reciprocating bodies 31 and 39 are connected to each other by means of a member P1253 / 96MX rigid cross 45 and with a multiplicity of hard springs 46 by means of an axially rigid and radially flexible solid rod 47. The flat spring is connected with a rigid housing 48 which is rigidly connected to the cylinder-32. The radially flexible member 47 reduces the radial force that fluid flowing from ducts 35, 36, 37 and 38 must generate to restore the reciprocating axis acceptably close to the etric axis of symmetry 49. Figure 7 illustrates, in axial section, an alternative practical embodiment of The invention, in which a thermomechanical transducer is mechanically connected to an electromechanical electromagnetic transducer, both have oscillating bodies mounted on springs that effect a reciprocating movement with respect to a radially adjacent cylinder. Again, the thermomechanical transducer is a free piston compressor and the electromechanical electromagnetic transducer is a linear motor. However, in this embodiment, the cylinder 61 of the compressor is hollow and contains a source of pressurized fluid for a fluid bearing. The fluid enters the hollow interior of the cylinder 61, from the compression space 62, through a unidirectional valve 63, and exits towards the space of separation between the reciprocating piston 64 and the cylinder 61 through the conduits P12E3 / 96MX 65, 66, 67 and 68. In this embodiment, the reciprocating body of the linear motor is the support structure 69a for an inductor coil 69b of electrically conductive wire that effect reciprocating movement with respect to the internal and external members of the motor. magnetic flux 70 and 71, which together constitute a magnetic flux path with two spaces 72 and 73 around an armature coil 74 of electrically conductive wire. A rigid treinsversal member 75 connects the inductor coil 69b and its linear motor support structure 69a to the center region of a multiplicity of flat mechanical springs 76, whose peripheral region is connected to the rigid housing 77 which is rigidly connected to the cylinder 61. A rigid transverse member 75 connects the inductor coil 69b and its supporting structure 69a of the linear motor to the central region of a multiplicity of flat mechanical springs 76, whose peripheral region is connected to the rigid housing 77 which is rigidly connected to the cylinder. 61. The rigid transverse member 75 is connected to the piston 64 of the compressor by means of an axially rigid and radially flexible rod 78. Again, the radially flexible member 78 reduces the radial force that the fluid flowing from the conduits 65, 66 , 67, and 68 of the fluid bearing must generate to restore the reciprocating axis acceptably P1253 / 96MX near the etric axis of symmetry 79. Figure 8 illustrates, in axial section, another practical embodiment of the invention in which a thermomechanical transducer is mechanically connected to an electromechanical electromagnetic transducer, both have spring mounted oscillating bodies, which they perform a reciprocating movement inside the radially adjacent cylinders. Again, the thermomechanical transducer is a free piston compressor and the electromechanical electromagnetic trinser is a linear motor. As in Figure 6, the reciprocating body of the compressor is a hollow piston 81 which effects a reciprocating movement with respect to a radially adjacent cylinder 82. Again, the interior of the piston 81 serves as a source of pressurized fluid for a bearing of fluid, the fluid entering the piston 81 from the compression space 83 through the unidirectional valve 84 and exiting towards the gap between the piston 81 and the cylinder 82 through the conduits 85, 86, 87 and 88. Again, the reciprocating body of the linear motor is a ring of magnets 89 which effects a reciprocating movement with respect to the inner and outer cylinders 90 and 91 comprised of material of high permeability, which together constitute a magnetic flux path with two P12E, 3 / 96MX spaces 92 and 93 around an armature coil 94 of electrically conductive wire. Again, the two reciprocating bodies 81 and 89 are connected to each other by means of a rigid transverse member 95. However, in this embodiment, the rigid transverse member 85 is connected to the central region of a common flat spring 96, by means of of a solid axial and radially rigid rod 97, and the peripheral region of the flat spring 96 is connected to the rigid housing 98 by means of a multiplicity of axially rigid and radially flexible rods 99, 100 and others not visible in this view in cross section axial. The rigid housing 98 is also connected with the inner and outer cylinders 90 and 91 and also with the cylinder 82. Again, the radially flexible member consisting of the rods 99, 100, etc., reduces the radial force that the fluid, which flows from the conduits 85, 86, 87 and 88 of the fluid bearing, it must generate to restore the reciprocating axis acceptably close to the geometric axis of symmetry 101. Figure 9 illustrates in axial section another practical embodiment of the invention in a Stirling engine of Free piston, which has two oscillating bodies mounted on springs that effect a reciprocating movement with respect to the radially adjacent cylinders and axi ally in line. An oscillating body is a device Hollow displacement P1253 / 96MX 141 containing a positively pressurized fluid source for a fluid bearing and the fluid enters the hollow interior of the displacement device 141, from the expansion space 142 through the unidirectional valve 143. The fluid exits through conduits 144, 145, 146, and 147 towards the separation opening between the displacement device 141 and the cylinder 148 of the displacement device. The reciprocating movement of the displacement device 141 sends the fluid back and forth through the heat-acceptor heat exchanger 149, the heat-expelling heat exchanger 150, and the regenerator 151. The displacement device 141 is connected with a spring helical mechanical 152 by means of an axially rigid and radially flexible solid rod 153. The cylinder 154 of the piston also contains a positively pressurized fluid source for a fluid bearing and the fluid enters the hollow interior of the cylinder 154 of the piston, from the space of compression 155 through the unidirectional valve 156. The fluid exits through the conduits 157, 158, 159 and 160 towards the gap between the cylinder 154 of the piston and the second oscillating body which is a piston 161. The movement reciprocating piston 161 compresses and expands alternatively to the fluid in the general region comprised P1253 / 96MX of the expansion space 142, of the heat-exchanger heat exchanger 149, of the heat expelling heat exchanger 150, of the regenerator 151 and of the compression space 155, thereby pneumatically coupling the reciprocating movement of the displacement device 141 with that of the piston 161. The piston 161 is connected to the central region of a single flat mechanical spring 162 by means of a. hollow, axially rigid and radially flexible rod 163, through which passes the solid, axially rigid and radially flexible rod, which connects the displacement device 141 with the rigid member 164, which radially restricts the movement of a separate multiplicity of springs helical mechanics 165a and 165b. The multiplicity of coil springs 165a and 165b of the displacement device and the flat spring 162 of the piston are both connected to the rigid housing 166 which is again connected to the cylinder 148 of the displacement device and to the cylinder 154 of the piston. Again, the radially flexible members 153 and 163 reduce the radial force, the fluid flowing from the conduits 144, 145, 146 and 147 of the fluid bearing of the displacement device and the conduits 157, 158, 159 and 160 of the bearing fluid of the piston, they must generate to restore the reciprocating axis of the displacement device 141 and of the piston 161 P1253 / 96MX acceptably close to the symmetrical axis of symmetry. Figure 10 illustrates, in axial section, another practical embodiment of the invention in a compressor having two oscillating bodies mounted on springs which effect a reciprocating movement with respect to the radially adjacent cylinders and axially in line. In this embodiment, the pistons 171 and 172 are mechanically connected to the axial member, which is axially and radially rigid 173, by means of axially rigid and radially flexible solid rods 174 and 175. The rigid axial member 173 is mechanically connected to the central regions of the flat springs 176 and 177, whose peripheral parts are connected to the housing portions 178 and 179 which are rigidly connected to the cylinders 180 and 181. The pistons 171 and 172 perform a reciprocating movement with respect to the radially adjacent cylinders 180 and 181, whose hollow interiors serve as sources of pressurized fluid. The fluid enters the hollow interiors of the cylinders 180 and 181 through the unidirectional valves 182 and 183 from the compression spaces 184 and 185 and exits towards the separation spaces between the pistons 171 and 172 and their cylinders 180 and 181, through conduits 186, 187, 188, 189, 190, 181, 191, 192 and 193. The rigid transverse member 194 connects the axial member 173 with a ring of magnets 195.

P1253 / 96MX which performs a reciprocating movement with respect to the inner and outer cylinders 196 and 197, of which the two are comprised of material of relatively high permeability and the constituent parts of the magnetic flux loop with separations 198 and 199, which surround an armature coil 200 of electrically conductive wire. The radially flexible members 174 and 175 reduce the radial force which, the fluid flowing from the conduits 186, 187, 188, 189, 190, 181, 192 and 193 of the fluid bearing, must generate to restore the reciprocating axes of the two pistons 171 and 172 acceptably close to the geometric axis of symmetry 201. Figure 11 illustrates in axial cross section two types of gas springs that may be incorporated in the invention. Figure HA shows a compression space 241 bordered by the side and end wall of the cylinder 242, within the housing 244 and by the disc 245. The cylinder 242 is substantially coaxial with a geometric axis of symmetry 243 along which the disc will make a reciprocating movement. The disc 245 is connected to the reciprocating body of a mechanical transducer by the axially rigid and laterally flexible member 246. The disc 245 is caused to reciprocate along an axis acceptably close to the axis of symmetry 243 P1253 / 96MX by the action of the fluid bearing comprised of the pressure chamber 247, the unidirectional valve 248, and the restricted conduits 249, 250, 251 and 252 all of which are located within the housing 264. Figure 11B shows a space of compression 261 bordered by the side and end wall of the cylinder 262 inside the housing 264 and by the hollow disk 265. The cylinder 262 is substantially coaxial with a geometric axis of symmetry 263 along which the disk will effect a reciprocating movement. The disc 265 is connected to the reciprocating body of a mechanical transducer by the axially rigid and laterally flexible member 266. The disc 265 is caused to reciprocate along an axis acceptably close to the axis of symmetry 263, by the action of the fluid bearing comprised of the pressure chamber 267, the unidirectional valve 268, and the restricted conduits 269, 270, 271 and 272, all of them are located within the disc 265. Figure 12 illustrates in axial cross-section a magnetic spring of the type described in detail in U.S. Patent No. 5,148,066. The magnetic spring is comprised of two magnetic flux loop members 231 and 232 which together comprise a magnetic flux loop with two circular spaces 233 and 234.

P1253 / 96MX What effects reciprocating movement within the spaces of the magnetic flux loop is a magnet vane 235 that holds three magnets. A radially polarized field electromagnet 236 establishes an alternating magnetic field within the magnetic flux loop as the magnet blade performs a reciprocating motion, axially within the spaces 233 and 234. On both sides of the field electromagnet 236 there are two spring magnets 237 and 238 which are also radially polarized, but in the opposite direction to the field electromagnet 236. The axial displacement of the magnet vane 235 in any direction causes the spring magnets to interact with the magnetic field of the field electromagnet, thereby that induces a proportional restoring force on the magnet blade. In practical embodiments, the magnetic flux loop members 231 and 232 would be attached to the housing and the magnet vane 235 would be attached, by an axially rigid and laterally flexible rod, to a reciprocating body. Alternatively, the magnet vane 235 would be attached by a rigid member to the reciprocating body and the magnetic flux loop members would be connected to the housing by an axially rigid and laterally flexible member. Figure 13 illustrates, in an oblique view or in P1253 / 96MX diagonally, a flat spring that can serve alone as the radially flexible member as well as the axially flexible energy storage element of the invention. In the practical embodiments of the invention, the region radially. peripheral 221 of the spring is attached to a housing rigidly continuing with the cylinder, with respect to which the oscillating body effects a reciprocating movement, while the central region 222 of the spring is joined to the reciprocating body by means of axially linked components and radially rigid. Alternatively, the peripheral region 221 may be attached to the reciprocal body while the central region 22 is attached to the housing. In the modalities using this spring, the axial flexibility of the spring substantially resonates the mass of the reciprocating body while the radial flexibility of the spring reduces the amount of force that the fluid bearings must generate to restore the reciprocating shaft acceptably close to the shaft. symmetry geometry 223. From the foregoing description it is clear that the invention can be used with a variety of bodies, including, pistons, displacement device and magnet vanes that perform a reciprocating movement, axially, in a junction chamber , such as a cylinder or the separation of a loop from P1253 / 96MX magnetic flux. The body is linked or linked to the housing, in which the camera is formed, by a linkage that includes one or more link or link components. At least one link component is axially flexible to apply an axial force on the body, normally to tune the system to close resonance. An antifriction fluid bearing minimizes contact between the chamber wall and the body, applying layered centering forces on the body. At least one linkage component is included which has sufficient lateral flexibility so that the centering forces of the fluid bearing are at least equal to the sum of the lateral force exerted on the body by the linkage, plus the other lateral forces exerted on the body. This allows the centering forces of the fluid bearing to be effective in moving the body away from the wall of the chamber and thereby minimizing consequent contact and wear. While certain preferred embodiments of the present invention have been presented in detail, it will be understood that various modifications may be made without departing from the spirit of the invention or the scope of the following claims.

P1253 / 96MX

Claims (14)

1. NOVELTY OF THE INVENTION Having described the present invention, it is considered as a novelty and, therefore, the content of the following CLAIMS is claimed as property: 1. An improved mechanical transducer having a housing that includes a camera defined by at least a wall and having a geometric axis of symmetry, the chamber contains a coupling body, which performs a reciprocating movement substantially axially, and is linked to the housing by means of a linkage comprising, at least, a linkage component which includes an axially flexible spring that applies an axial force on the body, the transducer has an antifriction bearing to minimize contact between the wall of the chamber and the body, wherein the improvement comprises that: (a) the bearing is a fluid bearing for applying lateral centering forces on the body; and (b) the linkage includes a component that has sufficient lateral flexibility so that the centering forces exerted by the fluid bearing are at least equal to the sum of all other lateral forces exerted on the body, including the lateral force exerted on the body. the body through P1253 / 96MX linkage, during normal operation of the transducer.
2. 2. A transducer according to claim 1, characterized in that the chamber is a cylinder and the body is a piston.
3. 3. A transducer according to claim 2, characterized in that the spring is a planar spring oriented orthogonal to the axis.
4. 4. A transducer according to claim 3, characterized in that the spring comprises a multiplicity of parallel flat springs attached near their perimeters and close to their centers.
5. 5. A transducer according to claim 3, characterized in that the spring is also the laterally flexible linkage component.
6. 6. A transducer according to claim 2, characterized in that the spring is a gas spring.
7. 7. A transducer according to claim 2, characterized in that the spring is a magnetic spring.
8. A transducer according to claim 2, characterized in that the spring is a multiplicity of at least three helical springs interconnected and spaced symmetrically about the axis.
9. 9. A transducer according to claim 2, characterized in that the linking component is P1253 / 96MX laterally flexible and comprises an axially rigid and radially flexible connector rod.
10. 10. A transducer according to claim 9, characterized in that the connecting rod is a tube. A transducer according to claim 9, characterized in that the laterally flexible link component comprises a plurality of axially rigid and radially flexible connecting rods spaced symmetrically about the axis. A transducer according to claim 2, characterized in that the radially flexible link component is axially rigid and is interposed between the piston and the spring. A transducer according to claim 2, characterized in that the laterally flexible link component is axially rigid and is interposed between the spring and the housing. A transducer according to claim 1, characterized in that the body is the magnet blade of a linear electromagnetic tricinsulator. P1253 / 96MX