EP1856413B1 - Tige d'entrainement destinee au piston d'un compresseur alternatif - Google Patents
Tige d'entrainement destinee au piston d'un compresseur alternatif Download PDFInfo
- Publication number
- EP1856413B1 EP1856413B1 EP06721573.1A EP06721573A EP1856413B1 EP 1856413 B1 EP1856413 B1 EP 1856413B1 EP 06721573 A EP06721573 A EP 06721573A EP 1856413 B1 EP1856413 B1 EP 1856413B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- driving rod
- rods
- set forth
- cross
- piston
- 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.)
- Expired - Fee Related
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
- F04B39/0022—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons piston rods
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
- F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
- F04B35/045—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric using solenoids
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/21—Elements
- Y10T74/2142—Pitmans and connecting rods
- Y10T74/2144—Yieldable
Definitions
- the present invention refers to a driving rod to be applied to a reciprocating compressor with an electric motor of the rotary or linear type, said driving rod being constructed to operatively couple a driving means to a piston to be reciprocated in the interior of a compression chamber of the compressor, according to the axis of said chamber.
- the reciprocating compressors that are driven by a rotary or linear electric motor generally comprise a cylinder block defining, internally, a compression chamber inside which axially reciprocates a piston coupled to a driving means mounted to the cylinder block and operatively associated with the electric motor of the compressor.
- the piston is coupled to the driving means so as to allow forces to be transferred therebetween and to make the piston move inside the compression chamber according to an axial direction coinciding with the axis of said compression chamber in order to minimize the transversal reaction forces of the cylinder block against the piston inside the compression chamber.
- the transversal reaction forces of the cylinder block against the piston can provoke excessive friction between the piston and the cylinder block, leading to an increase of energy consumption, consequently reducing the efficiency of the compressor, and to an accelerated wear of the components submitted to high friction levels, reducing the useful life of the compressor.
- a known reciprocating compressor with a linear electric motor as illustrated in figure 1 of the appended drawings, comprises a cylinder block 10 defining, internally, a compression chamber 11 presenting an axis 12 and with a piston 20 axially reciprocating therewithin.
- the compression chamber 11 has an end that is generally closed by a valve plate 13 and by a cylinder head 14, the valve plate 13 being provided with a suction valve 13a and a discharge valve 13b of adequate construction to control the admission and discharge of gas in relation to the compression chamber 11 upon the movement of the piston 20.
- the piston 20 is operatively coupled to a driving means DM, which in the case of a compressor with a linear electric motor, comprises an actuator 30 in the form of a tubular structure, concentric and external to the compression chamber 11 and carrying a magnetic element 31 to be operatively impelled, with the actuator 30, upon the energization of a linear electric motor 40 mounted to the cylinder block 10 around the compression chamber 11.
- the driving means further comprises a set of springs 60 mounted between the cylinder block 10 and the piston 20.
- a driving rod 50 whose opposite end is coupled to the springs 60, helical springs for example, which are mounted in such a way as to exert opposite axial forces on the piston 20 upon its axial reciprocating movement in the interior of the compression chamber 11 provoked by the driving means DM comprising the actuator 30 and the springs 60.
- the piston 20, the actuator 30 and the springs 60 form the resonant assembly of the compressor with a linear motor.
- compressors are designed and constructed so that the axis of the axial reciprocating movement of the piston 20 coincides with the axes of both the piston 20 and the compression chamber 11, aiming at minimizing or even suppressing the transversal reaction forces between the piston 20 and the cylinder block 10.
- said axes can become misaligned and thus undesirable transversal reaction forces may occur between the piston 20 and the cylinder block 10 by reason of some constructive characteristics inherent to the compressors, such as the geometrical errors in the construction of the helical springs and the transversal rigidity thereof when they are axially and elastically deformed.
- misalignments commonly occur in the construction and assembly of mechanical components, as perfection is not usually reached in terms of dimensions and forms of the different components of a mechanical device.
- the driving rod 50 has the form of a generally tubular and transversally rigid axial rod, whereby the piston-actuator assembly behaves as a single body onto which are applied magnetic axial forces of the linear motor 40 which do not produce, over the piston 20, transversal components capable of causing excessive friction between said piston 20 and the cylinder block 10.
- the springs 60 exert over the piston-actuator assembly, not only the axial forces resulting from the compression thereof during the movement of the piston 20, but also transversal forces whose intensity varies as a function of the errors of construction and assembly of the springs 60.
- Such undesirable transversal forces produced by the operational deformation of the springs, tend to misalign the piston 20 in relation to the axis of the compression chamber 11, giving rise to transversal reaction forces of the cylinder block 10, as well as a consequent higher friction between the latter and the piston 20 axially reciprocating within the compression chamber 11.
- Patent US 5,525,845 from Sumpower Inc., describes a constructive solution for the problem cited above, according to which the driving rod, which can be mounted in different manners between the piston and the driving means, is constructed so as to present a required axial rigidity and also a transversal flexibility sufficient to prevent all the transversal forces acting on the piston, including the force exerted by the driving rod itself, from surpassing the centralizing transversal forces applied to the piston by a pneumatic bearing provided between the latter and the cylinder block.
- This prior solution uses a single-piece driving rod dimensioned to present the necessary axial rigidity and a transversal flexibility in a degree compatible with the centralizing transversal forces produced on the piston by the pneumatic bearing. Said prior art solution do not permit an adequate flexibility in the dimensioning' of the driving rod in relation to compressors in which the axial force to be transmitted or supported by the driving rod requires a cross-section area for the latter which hinders, in the length available for the single-piece driving rod, the latter from presenting the desired transversal flexibility.
- the use of multiple rods is suggested ( figure 8 ) only in a spaced-apart relationship, each rod being dimensioned to present the desired characteristics of axial rigidity and transversal flexibility. This is a complex construction, requiring the provision of the pneumatic bearing to maintain the piston adequately centralized in the compression chamber.
- said prior art multiple rods do not absorb transversal forces produced by angular misalignments of the axis of the driving means in relation to the axis of the compression chamber.
- Such misalignments are not absorbed by the spaced-apart rods, since the latter would have to be axially deformed, partially by expansion and partially by construction.
- the required axial rigidity of the rods prevents them from being dimensioned to bend, reducing their length upon the occurrence of said angular misalignments.
- the reciprocating compressors with a connecting rod-crankshaft mechanism driven by a rotary motor also present problems related to geometrical and assembly errors.
- Such compressors also comprise a cylinder block 10 defining, internally, a compression chamber 11 with a reciprocating piston 20 axially moving therewithin.
- the compression chamber 11 presents an axis 12 and an end closed by a valve plate 33 provided with a suction valve 13a and a discharge valve 13b, and a cylinder head 14.
- the piston 20 is driven by a driving means DM, in the form of a crankshaft 35, rotatively supported in the cylinder block and mounted to a rotary motor (not illustrated), the crankshaft having an end receiving the larger eye of a driving rod 50 in the form of a connecting rod, whose smaller eye is rotatively supported on the known diametrical articulating pin 21 inside the piston 20.
- a driving means DM in the form of a crankshaft 35, rotatively supported in the cylinder block and mounted to a rotary motor (not illustrated), the crankshaft having an end receiving the larger eye of a driving rod 50 in the form of a connecting rod, whose smaller eye is rotatively supported on the known diametrical articulating pin 21 inside the piston 20.
- reaction forces FR can lead to the transmission of reaction forces FR transversal to the axis 12 of the compression chamber 11, a situation in which the piston 20 tends to work misaligned with said axis 12.
- reaction forces FR acting mainly in the direction of the articulating pin 21 of the piston 20, tend to produce undesirable levels of friction between the piston 20 and the cylinder block 10, increasing the consumption of energy in the operation of the compressor as well as the wear of the mutually frictional parts, reducing the reliability and the useful life of the machine.
- the solution taught by the prior art is to dimension the driving rod 50 with a cross-section which, in the length defined in the compressor project, leads to the necessary axial rigidity of the driving rod, so that the latter can withstand the transmission of forces between the driving means DM (crankshaft) and the piston 20, but which however gives to the driving rod 50, in the form of a connecting rod, a flexibility in a transversal direction which minimizes the transmission of moment to the piston 20.
- a driving rod presenting a construction that allows obtaining a flexibility, in at least one transversal direction, as well as an axial rigidity which can comply with the requirements of the compressor project regardless of the length defined for the driving rod.
- the driving rod proposed by the present invention offers a simple solution that is easy to implement in the construction of reciprocating compressors, particularly those of the hermetic type used is refrigeration systems of household electric appliances in which the piston is designed to be axially displaced in a reciprocating movement inside a compression chamber, without being submitted to transversal reaction forces of the cylinder block caused by the acceptable geometrical or assembly errors of the component parts involved, but which are sufficiently relevant to cause friction that abbreviates the useful life of the compressor.
- the present driving rod comprises a bundle of "n" rods arranged side by side along the axis of the driving rod, each rod presenting a cross-section that is dimensioned and configured to impart to the driving rod, jointly with the other rods, an axial rigidity sufficient to transmit the reciprocating forces between the driving means and the piston, and a flexibility, in at least one transversal direction to the axis of the driving rod, sufficient to absorb, at least substantially, the forces applied to the piston, in said transversal direction, by both the driving rod and the driving means in the region of the compression chamber.
- the number and the cross-section of the rods that form the driving rod can be defined to impart to the latter optimized axial rigidity and transversal flexibility so that the reciprocating movement of the piston inside the compression chamber of the cylinder block occurs with little or no friction that abbreviates the useful life of the compressor.
- the construction of the driving rod of the present invention is designed to be applied to reciprocating compressors driven by a linear motor or by a rotary motor.
- Figure 3 illustrates, basically, the same elements that constitute a reciprocating compressor with a linear motor, contained in figure 1 and identified by the same reference numbers, constructive differences existing only in relation to the construction and assembly of the driving rod 50.
- the driving means DM is defined by an actuator 30 and by a pair of springs 60, the actuator 30 comprising a basic structure 30a, transversal to the axis 12 of the compression chamber 11 and incorporating an internal tubular projection 30b, rigidly secured to the piston 20, and an external tubular projection 30c that carries the magnetic element 31, the driving rod 50 being constructed so as to have an end secured to the piston 20 and an opposite end secured to a support 70 to which are mounted the adjacent ends of two springs 60, which in the illustrated construction have a helical form concentric to the axis 12 of the compression chamber 11, the opposite ends of the two springs 60 being mounted to the cylinder block 10, so that the springs 60 can exert, over the support 70, opposite axial forces to be transmitted to the piston 20 by the driving rod 50 disposed according the axis 12 of the compression chamber 11.
- the support 70 can be constructed in different manners, but bearing in mind the necessity of its axial reciprocating movement, in conjunction with the piston 20 and with the adjacent ends of the springs 60, being effected with no interference of the driving means 30.
- the support 70 comprises a pair of shoes 71 disposed in planes that are parallel to each other, orthogonal to the axis 12 of the compression chamber 11 and located on opposite sides of the basic structure 30a of the actuator 30, said shoes 71 being axially interconnected by spacers 72 disposed through respective windows 33 provided in the basic structure 30a of the actuator 30.
- the exemplary construction illustrated in figure 3 makes the transversal forces produced by the springs 60, when the latter are elastically and axially deformed, to have the tendency to be transferred to the piston 20 through the driving rod 50.
- the driving rod 50 comprises a bundle "n" of rods 51 disposed side by side along the displacement axis of the piston 20, each rod 51 presenting a cross-section that is dimensioned and configured to impart to the driving rod 50, jointly with the other rods 51, an axial rigidity that is sufficient to transmit the axial forces to be applied to the piston 20 by the springs 60 upon movement of the actuator 30, as well as a flexibility, in at least one direction transversal to the axis of the driving rod 50, which is sufficient to absorb, at least substantially, the forces exerted over the piston 20, in said transversal direction, by the driving rod 50 and by the driving means DM in the region of the compression chamber 11.
- each rod 51 in the form of a bundle of rods 51 in an adequate material, usually steel, allows each rod 51 to be dimensioned with a cross-section area that corresponds to 1/n of a cross-section area necessary to give to the driving rod 50, in the length determined in project, an axial rigidity sufficient to withstand the required transmission of axial forces between the piston 20 and the driving means DM, which in the construction illustrated in figures 3-13 , comprises the actuator 30 and the springs 60.
- the cross-section of the rods 51 should be dimensioned and configured so that the sum of the moments of inertia of the rods 51, in the determined transversal direction, is an integer fraction of the moment of inertia, of said transversal direction, of a single piece driving rod having a cross-section area corresponding to the sum of the cross-section areas of the rods 51.
- the transversal rigidity (K2 res.) of the bundle of "n" rods 51 of circular section will correspond only to a fraction "n” of the transversal rigidity (K1) of a single-piece driving rod, with a cross-section area (A1) of the "n” rods 51 that form the bundle that defines the driving rod.
- the rods 51 are symmetrically disposed around the axis of the driving rod 50 and being usually rectilinear and parallel to each other.
- the rods 51 are provided in a helical arrangement, symmetrically disposed in relation to said axis and around the length of the driving rod 50.
- the rods 51 of the bundle of rods submitted to axial forces may be deformed, provoking collapse of the driving rod.
- the rods 51 of the bundle can be jointly and medianly surrounded by one or more sleeves 80, occupying part of the longitudinal extension of the driving rod 50.
- the sleeve 80 takes the form of an elastic ring 81, in a metallic of elastomeric material and dimensioned to press the rods K 2 ⁇ res .
- K 1 R 1 4 n
- R 1 4 1 n K 2 ⁇ res .
- the sleeve 80 is defined by a helical spring 82, metallic or elastomeric and which is tightly mounted around the bundle of rods 51 of the driving rod 50.
- the sleeve is defined by a tube extension 83, also made of any adequate material to impart to the driving rod 50 a certain transversal flexibility and which is mounted, with a small clearance, around the bundle of rods 51.
- the rods 51 present opposite ends which define the ends of the driving rod 50 and which are jointly secured in respective terminal blocks 90 which may present different constructions in different metallic or non-metallic materials;
- the terminal blocks 90 are configured to define the mounting means of the driving rod 50 in the piston 20 and in the support 70 of the springs 60.
- each terminal block 90 comprises a tubular body 91 that is usually externally threaded and incorporates an enlarged end head 91a, preferably in the form of a hexagonal end nut turned to the rods 51 and presenting, internally, a housing 91b axially defined through the enlarged end head 91a and through at least part of the length of the tubular body 91.
- This constructive arrangement also illustrated in figure 3 , allows the terminal blocks 90 to have the tubular body 91 thereof threaded in a corresponding threaded orifice 23, 73 provided in the piston 20 and in the support 70, respectively ( figure 3 ).
- the ends of the bundle of rods 51 are preferably tightly fitted and affixed by processes such as interference, welding, gluing, mechanical riveting or any other adequate process in the interior of the housing 91b of the respective tubular body 91.
- the terminal blocks 90 comprise an elongated body 92 externally threaded and incorporating an enlarged end head 92a.
- the ends 52 of the rods 51 are laterally curved, so that the terminal blocks 90 can be molded or injected in aluminum, plastic or any other adequate material, directly on said ends 52, guaranteeing the necessary mechanical anchorage between the driving rod 50 and the terminal blocks 90.
- each terminal block is formed by a pair of plates 93 to be secured to each other, sandwiching a respective end of the rods 51.
- One or both the plates 93 are internally provided with a recess 93a configured to receive and fit a respective cross-section portion of an extension of the adjacent end of the bundle of rods 51, said extension being laterally curved or bent to facilitate locking the end of the driving rod 50 in each terminal block 90.
- the plates 93 of each pair are preferably provided with orifices 93b for the passage of tightening screws (not illustrated).
- the driving rod 50 can be designed in the form of a connecting rod to operate in a reciprocating compressor of the type in which the piston 20 is driven by a driving means DM in the form of a crankshaft 35 (see figure 2 ).
- the terminal blocks 90 of the driving rod 50 are defined by eyes 94 to be respectively rotatively supported around the articulating pin 21 of both the piston 20 and the crankshaft 35.
- the driving rod 50 comprises a number "n" of rectilinear parallel rods 51 which are laterally seated in relation to each other, each rod 51 having a rectangular cross-section with a dimension L corresponding to a dimension "L” of the rectangular cross-section of a single-piece driving rod and with the other dimension "h” corresponding to the fraction "n” of the other dimension "H” of the cross-section of said single-piece driving rod.
- the same rectangular cross-section area of each rod 51 corresponds to the fraction "n" of the cross-section area of said single-piece driving rod.
- the same ratio is applied to the relation between the moment of inertia, in the axial direction of each rod 51 and the moment of inertia in the axial direction of the single-piece driving rod.
- the sum of the cross-section areas of the rods 51 corresponds to the cross-section area of said reference single-piece driving rod.
- the driving rod 50 with "n" rods 51 has an axial rigidity equivalent to that obtained with the driving rod formed by only one rod having a cross-section area corresponding to the sum of the cross-section areas of the "n" rods 51 of the driving rod 50 with multiple rods.
- H n e h H n
- the transversal rigidity (K2res.) of the bundle of "n' rods 51 with a rectangular section will correspond only to a fraction "n2" of the transversal rigidity (K1) of a single-piece driving rod presenting a cross-section area (A1) corresponding to the sum of the cross-section areas (A2) of the "n” rods 51 that form the bundle that defines the driving rod 50 of the invention, as well as a cross-section dimension "H", in said direction, corresponding to the sum of the corresponding cross-section dimensions (h) of the rods 51 that form the driving rod 50.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Claims (21)
- Tige d'entraînement pour le piston d'un compresseur alternatif du type qui comprend : un bloc cylindres (10) définissant, à l'intérieur, une chambre de compression (11) ; un piston (20) effectuant un mouvement alternatif axial à l'intérieur de la chambre de compression (11) selon l'axe de celle-ci ; un moyen d'entraînement (DM) monté dans le bloc cylindres (10) pour appliquer des forces alternatives sur le piston (20) ; et une tige d'entraînement (50) couplée au piston (20) et au moyen d'entraînement (DM), caractérisée en ce que la tige d'entraînement (50) comprend un faisceau de « n » tiges (51) disposées côte à côte le long de l'axe de la tige de piston (50), chaque tige (51) présentant une section transversale qui est dimensionnée et configurée pour conférer à la tige d'entraînement (50), conjointement avec les autres tiges (51), une rigidité axiale suffisante pour transmettre les forces alternatives à appliquer au piston (20), ainsi qu'une flexibilité, dans au moins une direction transversale à l'axe de la tige de piston (50), qui est suffisante pour absorber, au moins en grande partie, les forces exercées sur le piston (20), dans ladite direction transversale, par la tige d'entraînement (50) et par le moyen d'entraînement (DM) dans la région de la chambre de compression (11).
- Tige d'entraînement selon la revendication 1, caractérisée en ce que chacune des tiges (51) présente une aire de section transversale correspondant à 1/n de l'aire de section transversale nécessaire pour conférer à la tige d'entraînement (50) la rigidité axiale suffisante, la section transversale des tiges (51) étant dimensionnée et configurée de manière à ce que la somme des couples d'inertie des tiges (51), dans ladite direction transversale, soit une fraction du couple d'inertie, dans ladite direction transversale, d'une tige d'entraînement monopièce ayant une aire de section transversale correspondant à la somme des aires de section transversale des tiges (51).
- Tige d'entraînement selon la revendication 2, caractérisée en ce que la somme des couples d'inertie des tiges (51) correspond à une fraction « n » du couple d'inertie d'une tige d'entraînement monopièce (50) ayant une aire de section transversale correspondant à la somme des aires de section transversale des tiges (51).
- Tige d'entraînement selon la revendication 2, caractérisée en ce que la somme des couples d'inertie des tiges (51) correspond à une fraction « n2 » du couple d'inertie d'une tige d'entraînement monopièce (50) ayant une aire de section transversale correspondant à la somme des aires de section transversale des tiges (51).
- Tige d'entraînement selon la revendication 2, caractérisée en ce que les tiges (51) sont disposées symétriquement autour de l'axe de déplacement du piston (20) et placées latéralement les unes par rapport aux autres.
- Tige d'entraînement selon la revendication 5, caractérisée en ce que les tiges (51) sont rectilignes et parallèles les unes par rapport aux autres.
- Tige d'entraînement selon la revendication 5, caractérisée en ce que les tiges (51) sont disposées selon un agencement hélicoïdal.
- Tige d'entraînement selon la revendication 5, caractérisée en ce que les tiges (51) présentent une section transversale circulaire ayant une flexibilité égale dans toute direction transversale.
- Tige d'entraînement selon la revendication 2, caractérisée en ce que les tiges (51) sont placées de manière rectiligne, parallèle et latérale les unes par rapport aux autres, chaque tige (51) ayant une section transversale rectangulaire avec une dimension correspondant à une dimension (L) de la section transversale rectangulaire d'une tige d'entraînement monopièce, et avec l'autre dimension (h) correspondant à la fraction « n » de l'autre dimension (H) de la section transversale de ladite tige d'entraînement monopièce, la section transversale de celle-ci correspondant à la somme des aires de section transversale des « n » tiges (51) de la tige d'entraînement ayant de multiples tiges (51).
- Tige d'entraînement selon la revendication 2, caractérisée en ce que les tiges (51) sont entourées de manière conjointe et médiane par au moins un manchon (80) occupant une partie de l'extension longitudinale de la tige d'entraînement (50).
- Tige d'entraînement selon la revendication 10, caractérisée en ce que le manchon (80) est défini par une bague élastique (81) appuyant les tiges (51) les unes contre les autres.
- Tige d'entraînement selon la revendication 10, caractérisée en ce que le manchon (80) est défini par un ressort hélicoïdal (82) monté serré autour des tiges (51) de la tige d'entraînement (50).
- Tige d'entraînement selon la revendication 10, caractérisée en ce que le manchon (80) est défini par une extension en tube (83) montée avec un faible jeu autour des tiges (51) de la tige d'entraînement (50).
- Tige d'entraînement selon la revendication 2, caractérisée en ce que les tiges (51) présentent des extrémités opposées définissant les extrémités de la tige d'entraînement (50), lesdites tiges (51) ayant chacune des extrémités opposées fixées conjointement à un bloc terminal (90).
- Tige d'entraînement selon la revendication 14, caractérisée en ce que chaque bloc terminal (90) comprend un corps tubulaire (91) incorporant une tête à extrémité agrandie (91 a) tournée vers les tiges (51) et présentant, en interne, un logement (91 b) défini axialement à travers la tête à extrémité agrandie (91 a) et à travers au moins une partie de l'extension du corps tubulaire (91).
- Tige d'entraînement selon la revendication 15, caractérisée en ce que le corps tubulaire (91) a un filetage externe, la tête à extrémité agrandie (91a) ayant la forme d'un écrou hexagonal.
- Tige d'entraînement selon la revendication 14, caractérisée en ce que les extrémités opposées (52) des tiges (51) sont courbées latéralement, définissant une déformation d'ancrage, chaque bloc terminal (90) étant moulé sur l'une des extrémités opposées (52) des tiges (51).
- Tige d'entraînement selon la revendication 17, caractérisée en ce que chaque bloc terminal (90) comprend un corps allongé (92) incorporant une tête à extrémité agrandie (92a) tournée vers les tiges (51).
- Tige d'entraînement selon la revendication 18, caractérisée en ce que le corps allongé (92) a un filetage externe, la tête à extrémité agrandie (92a) ayant la forme d'un écrou hexagonal.
- Tige d'entraînement selon la revendication 14, caractérisée en ce que les blocs terminaux (90) sont chacun formés par une paire de plaques (93) à fixer l'une à l'autre, prenant en sandwich une extrémité respective des tiges (51).
- Tige d'entraînement selon la revendication 14, caractérisée en ce que les blocs terminaux (90) sont définis par des orifices (94) d'une tige d'entraînement (50) ayant la forme d'une tige de connexion d'un compresseur alternatif.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
BRPI0500338-5A BRPI0500338A (pt) | 2005-02-01 | 2005-02-01 | haste de acionamento para pistão de compressor alternativo |
PCT/BR2006/000011 WO2006081642A2 (fr) | 2005-02-01 | 2006-02-01 | Tige d'entrainement destinee au piston d'un compresseur alternatif |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1856413A2 EP1856413A2 (fr) | 2007-11-21 |
EP1856413B1 true EP1856413B1 (fr) | 2015-07-15 |
Family
ID=36777584
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06721573.1A Expired - Fee Related EP1856413B1 (fr) | 2005-02-01 | 2006-02-01 | Tige d'entrainement destinee au piston d'un compresseur alternatif |
Country Status (8)
Country | Link |
---|---|
US (1) | US20080134833A1 (fr) |
EP (1) | EP1856413B1 (fr) |
JP (1) | JP5053866B2 (fr) |
KR (1) | KR101308114B1 (fr) |
CN (1) | CN100513782C (fr) |
BR (1) | BRPI0500338A (fr) |
ES (1) | ES2545478T3 (fr) |
WO (1) | WO2006081642A2 (fr) |
Families Citing this family (29)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102006009270A1 (de) | 2006-02-28 | 2007-08-30 | BSH Bosch und Siemens Hausgeräte GmbH | Linearverdichter mit vorgespannter Federkolbenstange sowie Kältemaschine |
BRPI0902557B1 (pt) * | 2009-07-08 | 2020-03-10 | Embraco Indústria De Compressores E Soluções E Refrigeração Ltda. | Compressor linear |
US20110252960A1 (en) * | 2011-04-27 | 2011-10-20 | Flight Medical Innovations Ltd. | Mechanical ventilator |
BRPI1103357A2 (pt) * | 2011-07-04 | 2013-07-23 | Whirlpool Sa | haste ou biela para compressor linear |
BRPI1103355A2 (pt) * | 2011-07-04 | 2013-07-23 | Whirlpool Sa | dispositivo adaptador para compressor linear, e compressor provido do referido dispositivo |
BRPI1103647A2 (pt) * | 2011-07-07 | 2013-07-02 | Whirlpool Sa | disposiÇço entre componentes de compressor linear |
BRPI1104172A2 (pt) * | 2011-08-31 | 2015-10-13 | Whirlpool Sa | compressor linear baseado em mecanismo oscilatório ressonante |
US20150226210A1 (en) * | 2014-02-10 | 2015-08-13 | General Electric Company | Linear compressor |
US9470223B2 (en) | 2014-02-10 | 2016-10-18 | Haier Us Appliance Solutions, Inc. | Method for monitoring a linear compressor |
US9562525B2 (en) | 2014-02-10 | 2017-02-07 | Haier Us Appliance Solutions, Inc. | Linear compressor |
US9506460B2 (en) | 2014-02-10 | 2016-11-29 | Haier Us Appliance Solutions, Inc. | Linear compressor |
US9528505B2 (en) | 2014-02-10 | 2016-12-27 | Haier Us Appliance Solutions, Inc. | Linear compressor |
US9322401B2 (en) | 2014-02-10 | 2016-04-26 | General Electric Company | Linear compressor |
US9739270B2 (en) | 2014-02-10 | 2017-08-22 | Haier Us Appliance Solutions, Inc. | Linear compressor |
US9518572B2 (en) * | 2014-02-10 | 2016-12-13 | Haier Us Appliance Solutions, Inc. | Linear compressor |
US10036370B2 (en) | 2014-02-10 | 2018-07-31 | Haier Us Appliance Solutions, Inc. | Linear compressor |
US9841012B2 (en) | 2014-02-10 | 2017-12-12 | Haier Us Appliance Solutions, Inc. | Linear compressor |
US9429150B2 (en) | 2014-02-10 | 2016-08-30 | Haier US Appliances Solutions, Inc. | Linear compressor |
CN105351168B (zh) * | 2014-08-19 | 2019-08-09 | 青岛海尔智能技术研发有限公司 | 一种线性压缩机的活塞结构以及线性压缩机 |
US9702352B2 (en) | 2014-10-27 | 2017-07-11 | Haier Us Appliance Solutions, Inc. | Linear compressor and a spring assembly |
US10502201B2 (en) | 2015-01-28 | 2019-12-10 | Haier Us Appliance Solutions, Inc. | Method for operating a linear compressor |
US10208741B2 (en) | 2015-01-28 | 2019-02-19 | Haier Us Appliance Solutions, Inc. | Method for operating a linear compressor |
US10174753B2 (en) | 2015-11-04 | 2019-01-08 | Haier Us Appliance Solutions, Inc. | Method for operating a linear compressor |
US10830230B2 (en) | 2017-01-04 | 2020-11-10 | Haier Us Appliance Solutions, Inc. | Method for operating a linear compressor |
US10641263B2 (en) | 2017-08-31 | 2020-05-05 | Haier Us Appliance Solutions, Inc. | Method for operating a linear compressor |
US10670008B2 (en) | 2017-08-31 | 2020-06-02 | Haier Us Appliance Solutions, Inc. | Method for detecting head crashing in a linear compressor |
KR102268253B1 (ko) * | 2019-10-24 | 2021-06-23 | 엘지전자 주식회사 | 압축기 |
KR102269942B1 (ko) | 2020-01-15 | 2021-06-28 | 엘지전자 주식회사 | 압축기 |
KR102269940B1 (ko) * | 2020-01-16 | 2021-06-28 | 엘지전자 주식회사 | 압축기 |
Family Cites Families (23)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1147266A (en) * | 1915-02-01 | 1915-07-20 | Gustav Rapsch | Emergency lubricating device. |
US1208430A (en) * | 1916-03-15 | 1916-12-12 | Wilson B Wigle | Resilient connector-weight. |
US1593430A (en) * | 1925-04-25 | 1926-07-20 | Charles R Bryson | Drill-jar piston |
US1817255A (en) * | 1925-05-29 | 1931-08-04 | Jesse G Hawley | Coupling |
US1785559A (en) * | 1927-10-28 | 1930-12-16 | Arthur J Ponti | Stress and strain compensating joint for rotary well-drilling columns |
SE345966B (fr) * | 1970-04-23 | 1972-06-19 | Goeteborga Bandvaeveri | |
US3822609A (en) * | 1972-04-17 | 1974-07-09 | Ustar Pro Uyzkum Motorovych Vo | Connecting rod |
US4002935A (en) * | 1975-05-15 | 1977-01-11 | A. O. Smith Corporation | Reciprocating linear motor |
JPS569678A (en) * | 1979-07-04 | 1981-01-31 | Hitachi Ltd | Entirely-enclosed electric compressor |
JPS5631537A (en) * | 1979-08-17 | 1981-03-30 | Honda Motor Co Ltd | Connecting rod for internal combustion engine |
JPS6054780U (ja) * | 1983-09-20 | 1985-04-17 | トキコ株式会社 | 空気圧縮機の連接棒 |
US4538964A (en) * | 1984-01-04 | 1985-09-03 | Mechanical Technology Incorporated | Multistage resonant compressor |
JPS61274171A (ja) * | 1985-05-27 | 1986-12-04 | Honda Motor Co Ltd | シリンダ装置 |
JPS6221486U (fr) * | 1985-07-25 | 1987-02-09 | ||
US4805483A (en) * | 1986-06-28 | 1989-02-21 | Volkswagen Ag | Connecting rod with a shank composed of fiber composite material |
CN2105573U (zh) * | 1991-08-05 | 1992-05-27 | 高信泉 | 往复式双缸压缩机 |
US5525845A (en) * | 1994-03-21 | 1996-06-11 | Sunpower, Inc. | Fluid bearing with compliant linkage for centering reciprocating bodies |
KR100224186B1 (ko) * | 1996-01-16 | 1999-10-15 | 윤종용 | 선형 압축기 |
WO1998001675A1 (fr) * | 1996-07-09 | 1998-01-15 | Sanyo Electric Co., Ltd. | Compresseur lineaire |
BR9802053A (pt) * | 1998-05-04 | 2000-03-08 | Brasil Compressores Sa | Biela bi-partida para compressor alternativo e método de montagem de biela bi-partida. |
JP2001227461A (ja) * | 2000-02-14 | 2001-08-24 | Matsushita Electric Ind Co Ltd | リニア圧縮機 |
BR0201189B1 (pt) * | 2002-03-22 | 2010-06-29 | compressor alternativo acionado por motor linear. | |
JP4258282B2 (ja) * | 2002-08-30 | 2009-04-30 | 株式会社豊田自動織機 | 容量可変型斜板式圧縮機 |
-
2005
- 2005-02-01 BR BRPI0500338-5A patent/BRPI0500338A/pt not_active IP Right Cessation
-
2006
- 2006-02-01 ES ES06721573.1T patent/ES2545478T3/es active Active
- 2006-02-01 US US11/813,602 patent/US20080134833A1/en not_active Abandoned
- 2006-02-01 EP EP06721573.1A patent/EP1856413B1/fr not_active Expired - Fee Related
- 2006-02-01 KR KR1020077017071A patent/KR101308114B1/ko not_active IP Right Cessation
- 2006-02-01 CN CNB2006800037762A patent/CN100513782C/zh not_active Expired - Fee Related
- 2006-02-01 WO PCT/BR2006/000011 patent/WO2006081642A2/fr active Application Filing
- 2006-02-01 JP JP2007552472A patent/JP5053866B2/ja not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
JP5053866B2 (ja) | 2012-10-24 |
WO2006081642A8 (fr) | 2007-10-25 |
CN100513782C (zh) | 2009-07-15 |
KR101308114B1 (ko) | 2013-09-12 |
BRPI0500338A (pt) | 2006-09-12 |
JP2008528858A (ja) | 2008-07-31 |
WO2006081642A2 (fr) | 2006-08-10 |
EP1856413A2 (fr) | 2007-11-21 |
CN101128669A (zh) | 2008-02-20 |
WO2006081642A3 (fr) | 2006-12-28 |
KR20070098879A (ko) | 2007-10-05 |
ES2545478T3 (es) | 2015-09-11 |
US20080134833A1 (en) | 2008-06-12 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP1856413B1 (fr) | Tige d'entrainement destinee au piston d'un compresseur alternatif | |
EP1488104B1 (fr) | Compresseur alternatif entraine par un moteur lineaire | |
US6540490B1 (en) | Reciprocating compressor driven by a linear motor | |
EP1520106B1 (fr) | Agencement resonant pour compresseur lineaire | |
EP1362186B1 (fr) | Compresseur volumetrique alternatif a moteur lineaire | |
EP2659139A1 (fr) | Mécanisme résonant destiné à des compresseurs linéaires | |
US5671655A (en) | Two-piece connecting rod for a reciprocating hermetic compressor | |
WO2001018393A1 (fr) | Ensemble resonnant pour compresseur alternatif a moteur lineaire | |
US20100162733A1 (en) | Linear Compressor With Preloaded Spring Piston Rod, and Refrigerating Machine | |
JP2004522054A (ja) | リニアコンプレッサ | |
WO2000070223A1 (fr) | Compresseur a mouvement alternatif entraine par un moteur lineaire | |
EP2052155B1 (fr) | Agencement piston-tige d'entraînement pour compresseur alternatif | |
EP0836004B1 (fr) | Compresseur | |
WO2004081406A2 (fr) | Ressort helicoidal et compresseur alternatif le comprenant | |
KR100834768B1 (ko) | 사판식 압축기의 메커니즘 스프링 및 그 사판식 압축기 | |
WO2008072812A1 (fr) | Mécanisme à ressort et compresseur de type à plateau oscillant l'utilisant | |
KR20050019810A (ko) | 리니어 압축기용 공진 장치 | |
JP2000297752A (ja) | 振動式圧縮機 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20070727 |
|
AK | Designated contracting states |
Kind code of ref document: A2 Designated state(s): DE ES FR IT |
|
R17D | Deferred search report published (corrected) |
Effective date: 20071025 |
|
DAX | Request for extension of the european patent (deleted) | ||
RBV | Designated contracting states (corrected) |
Designated state(s): DE ES FR IT |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
INTG | Intention to grant announced |
Effective date: 20150218 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE ES FR IT |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 602006045975 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: ES Ref legal event code: FG2A Ref document number: 2545478 Country of ref document: ES Kind code of ref document: T3 Effective date: 20150911 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 602006045975 Country of ref document: DE |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20160309 Year of fee payment: 11 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20160418 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20161028 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160229 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160201 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 602006045975 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170901 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: ES Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160202 |
|
REG | Reference to a national code |
Ref country code: ES Ref legal event code: FD2A Effective date: 20181207 |