WO1979000386A1 - Improvements to cylinder heads of piston compressors,particularly for refrigerating fluids - Google Patents
Improvements to cylinder heads of piston compressors,particularly for refrigerating fluids Download PDFInfo
- Publication number
- WO1979000386A1 WO1979000386A1 PCT/FR1978/000034 FR7800034W WO7900386A1 WO 1979000386 A1 WO1979000386 A1 WO 1979000386A1 FR 7800034 W FR7800034 W FR 7800034W WO 7900386 A1 WO7900386 A1 WO 7900386A1
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- WIPO (PCT)
- Prior art keywords
- compressor
- cylinder head
- valve
- spacer
- piston
- Prior art date
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Classifications
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- 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
- F04B39/10—Adaptations or arrangements of distribution members
- F04B39/1053—Adaptations or arrangements of distribution members the members being Hoerbigen valves
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- 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
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
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- 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
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
- F04B49/24—Bypassing
- F04B49/243—Bypassing by keeping open the inlet valve
Definitions
- the present invention due to the collaboration of Mr. Institut LEORAT, relates to the arrangement of the cylinder heads of piston compressors, in particular for refrigerant and, in particular, to the control of the cooling power reduction devices for compressors equipped with movable cylinder heads "against liquid” and fitted with automatic valves with central aspiration.
- the object of the present invention consists, on the contrary, in an integrated construction leading to a minimum number of constituent parts, which results in very simple assembly and maintenance interventions, low cost of production and very good operating reliability. , this last point being of particular importance in industrial refrigeration applications.
- FIGS. 1 to 7 represent views in section along the axis of a cylinder, perpendicular to the axis of the crankshaft.
- - Figure 1 describes an embodiment of the invention compatible with a movable cylinder head having for elastic element a helical spring.
- FIG. 2 shows a variant of the embodiment of Figure 1 where the function of the coil spring is provided by Belleville washers.
- FIG. 3 shows an embodiment of the invention leading to a cylinder head with hydraulic pressurization and safety device by pieces with programmed failure.
- FIG. 4 shows an application of the invention to a compressor construction called "dry pistons”.
- FIG. 5 shows a valve structure, variant of the previous construction.
- FIG. 7 shows a variant of the previous device in which the cylinder head of the dry piston compressor is formed from a braced stack of two compressor cylinder heads of the lubricated type, the lower cylinder head being inverted.
- the automatic valve 3 rests on the collar of the jacket 2 of the cylinder. It is held in this position by means of the support piece 5- This piece can slide vertically in the corresponding bore of the cylinder head 51.
- the ribs 35 of the support piece 5 delimit profiled passages through which gases from the manifold 60 circulate when, on admission, they are sucked by the piston 1 to. through the orifices 42 of the valve 3.
- the ribs 35 support, in the upper part of the support piece 5, a bore 33 outside of which bears, on the flange 37, a helical spring 31. At its upper end, the spring 31 rests on a flat bearing ring, machined in a preferred embodiment of the invention, at the same time as the joint plane of the cylinder head cover 19. Inside the cylinder33 slides a piston 30, the rod of which comes press, in the low position, on the power reduction device 4 known per se.
- This device pushes the closure plate 44 of the valve 3 through the legs 41, which prevents the obturation of the intake ports 42 during the compression phase; under these conditions, instead of the refrigerant being compressed and discharged into the exhaust manifold 50 through the orifices 46, the fluid flows back into the intake enclosure.
- the piston 30 is supplied with service fluid, distributed for example by a solenoid valve not shown, by the channel 34 located in the cylinder head 51, then by the channel 9 pierced in the thickness of one of the ribs 35 and which opens into the groove 8 machined at the periphery of the support piece 5.
- the seal between the cylinder head 51 and the support piece 5 is provided by the two seals 6 and 7 which simultaneously seal the supply circuit of the piston 30 and the seal between the inlet 60 and discharge 50 enclosures of the working fluid.
- the single support piece 5 simultaneously fulfills the functions of:
- the invention is advantageously combined with a simultaneous surfacing of the joint plane of the cover 19 of the cylinder head and of the bearing rings on the cover 19 of the springs 31 and 16.
- the dispersion on the tares in place is, consequently, reduced to a minimum.
- This advantage is even more decisive when, for considerations of overall height, it is desirable to replace the helical spring 31 of the Belleville diaphragms 36 in parallel (this variant embodiment of the invention is illustrated in FIG. 2); indeed, this assembly requires excellent precision for the positioning of the diaphragms to ensure, in particular, that the stress rate remains acceptable over the entire length of the stroke.
- FIG. 3 shows how the invention can be applied directly to the concept of cylinder head with rupture part.
- the support piece 5 retains the same general morphology as in FIGS.
- the piston 11 which moves inside the cylinder 33 slides freely on the rod 10.
- the lower end of this rod presses, in the low position, on the power reduction device 4, while at its upper threaded end it is fixed by the bolt 17 to the bottom of the part 18.
- the part 18 has a cylindrical recess which serves as a housing for the spring 16 which rests on a flat crown 21 machined at the same time in a preferred embodiment than the joint plane of the cylinder head cover 19.
- the part 18 has a certain number of radiating arms 22 which lead to a circular crown 14 which rests, by means of studs 23, on the upper face of the piston 11.
- the arms 22 have in their middle a weakened section 15 calculated so as to rupture under a precomputed force as upper limit of the admissible thrust by the organs of the compressor of which it will be the first part to rupture beyond this thrust allowing, in addition, its load shedding as in the examples previously described.
- the spring 16 When the piston 11 is not supplied with working fluid, the spring 16 maintains the piston 11, part 18, rod 10 assembly in the low position and the power reduction device 4 is actuated.
- the spring 16 is calculated so that, in the position described above, the valve 3 is held without beating on the flange 2 when the compressor is running empty.
- the piston 11, rod 10, part 18 assembly moves to the high position, the part 18 coming to bear on the crown 21; the power reduction device 4 is then released and the load shedding removed.
- the valve 3 - part 5 a assembly tendency to lift.
- the liquid blow is of low intensity, it may be that the elasticity of the working fluid enclosed between the cylinder 33 and the piston as well as the volume of fluid discharged through the conduits 9 and 34 allow a sufficient lifting of the valve 3. Otherwise, the force transmitted is such that the arms 22 break at the weakened sections 15.
- the piston 11 then comes into abutment on the crown 21 by means of studs 23; the part 18, detached from the piston 11, descends under the force of the spring 16 and, by means of the rod 10, actuates the device 4 for reducing power; thus in the event of a liquid blow, the cylinder concerned of the compressor is automatically put to discharge after rupture of the safety part at the level of sections 22.
- the geometry of part 18 is such that, even after rupture, the two sections remain held in place and cannot cause damage to another part of the compressor.
- the movable "liquid blow" cylinder head for a central suction valve is characterized by a single piece, the intermediate piece 5, which transmits the bearing force of the main return spring ( helical or Belleville), guiding the power reduction control piston and supplying said control piston.
- the seals of the circuit supplying the control piston simultaneously seal the high and low pressure chambers of the compressor.
- the compressor starts automatically at zero load if the service fluid is the lubricating oil of the compressor whose pressurization will then release the load-shedding valve.
- the improvement to the cylinder heads of reciprocating piston compressors with central aspiration wedged on the sleeve flange in elastic abutment against the cylinder head cover in the configuration known as "liquid shock" according to the invention is characterized in that that the support by elastic wedging of the valve 3 on the liner 2 is produced by means of an intermediate piece 5 whose contact surfaces on the cylinder head 51 and on the valve 3 form a sealed separation 35 from the high and low pressure chambers compressor.
- this improvement to the compressor compressor piston heads with central suction valve wedged on the sleeve flange in elastic support against the cylinder head cover in the so-called "liquid shock" configuration is characterized in that the support with elastic setting of the valve 3 on the liner 2 is produced by an intermediate piece 5 in which is arranged a pusher (30, 10) for controlling a load shedding device 4, 41, 43, 44. actuated by the thrust elastic means 16, put out of service in normal operation by a reverse thrust of a service fluid supplied by conduits 9, 34 into a bore arranged in the intermediate part 5, thrust being exerted on a piston secured to the plunger 30, 10 against said elastic means 16.
- the intermediate part 5 slides while preserving the seal 6, 7 between the low and high pressure chambers of the compressor in a bore of the cylinder head 51 also receiving the central suction valve 3.
- the sliding seal of the intermediate piece 5 is ensured by at least two seals 6, 7 between which a circular groove 8 communicates with a pipe 34 of the cylinder head 51 bringing the service fluid under pressure and with a pipe 9 of the piece intermediate 5 bringing this fluid into the bore of the piston integral with the control pusher 30.
- the bearing rings on the cylinder head cover of the elastic means 16, 31, acting on the pusher 30 and the intermediate piece 5, are advantageously machined by the same plane dressing as that of the bearing surface of the cover 19, 62 of cylinder head 51.
- the device makes it possible to use, with good thrust precision, as elastic thrust means bearing on the intermediate part 5, a stack of Belleville washers 36 mounted between machined parallel planes.
- the elastic support of the intermediate piece 5 against the cover 19 realizing the setting of the valve 3 on the jacket 2 can be ensured by the pressure of the service fluid also ensuring the withdrawal of the pusher actuating the load shedding device 10 by l 'through a rupture part 23, 15, 22, 18 in direct support on the cover 19.
- the device is particularly applicable to the cylinder head of a dry double-acting compressor in which the jacket 65 is closed by two support parts 5, 69, the assembly being stacked in the same bore of a cylinder head 61 , 83 and supported on a cover-spacer 62 covering the piston block 81 of a basic lubricated compressor model, to which the dry pistons 66 are coupled by rods 78 sliding in leaktight manner through the intermediate parts 69 and the lower valves 63.
- the lower intermediate part 69 is then machined to receive a sealing device 70 for passage of the rod 78 connecting the pistons 66, 81 in place of the control system for the load shedding pusher 30.
- This lower intermediate piece 69 may be in leaktight support 75 on a machined surface of the spacer-cover 62 or slidably sealed 88 in a bore of the spacer-cover 62 in the event of accidental lifting of the lower valve 63 against an elastic means 87 , the dry compressor being thus provided, in both directions, with a "liquid blow” valve, the jacket 65 then being blocked in translation by a stud engaged in a groove 90 in its bore of the cylinder head 61.
- the lower valve 63 will have its two plates 92, 93 assembled by a central threaded sleeve 64 whose central internal bore where the piston connecting rod 78 slides is provided with seals 87.
- the cylinder head 61, 83 of the dry compressor will advantageously be formed by two cylinder heads 51 of compressors of the lubricated piston type, stacked and separated by a spacer 91 receiving the liners 65, the lower cylinder head 51 resting in the inverted position on the spacer-cover plate 62 of the base block.
- this improvement will apply to double-acting compressor heads built on a single-acting compressor base, characterized in that the double-acting compressor head consists of two single-acting compressor heads 51 stacked and separated by a spacer 91 receiving the sleeves 65 of the double-acting cylinders, the lower cylinder head 51 resting in the inverted position on a spacer-cover plate 62 of the base block.
- FIG. 4 which shows a section along the axis of a cylinder, perpendicular to the axis of rotation of the crankshaft, illustrates an embodiment of the invention applied to a dry piston compressor, double acting, based on a compressor with lubricated pistons of the type seen above and advantageously from a heat engine as described in French patent n ° 77/30663.
- the invention would also apply, without modifications other than those relating to the common field of those skilled in the art, to any type of compressor having a removable cylinder head.
- a compressor with lubricated pistons as described in the aforementioned French patent, the specific cylinder head of this compressor is replaced by a spacer 62 fixed in place of the bolts 74 and which keeps the removable jacket in place 2.
- a rod 78 is screwed into the piston 81 and locked in rotation by the lock nut 80.
- the spacer 62 has, at each cylinder, openings 77 allowing free passage of the gases during the translational movements of the pistons 81.
- the L 'spacer 62 bearing on the frame 84 of the upper opening of the sealed enclosure 85, supports the cylinder head 61 specific to the double-acting dry piston compressor, the bolts 82 subject are simultaneously the cylinder head 61 and the spacer 62 at the frame 84.
- the cylinder head 61 has a bore 86 in which are housed, listing from bottom to top: a support piece 69, an automatic valve 63, u ne removable jacket 65 forming a spacer, an automatic valve 3, a support piece 5, this ⁇ ant stack kept in place by the spring 31 which bears on the cover 19.
- the support piece 69 does not differ from the support part 5 only by the internal bore which serves as housing, in the case of part 69, to the stuffing box 70 ensuring sealing at the level of the rod 78 and by the presence, at its upper part, of the grooves containing the seals 75 which seal between the suction manifold 71 and the lower part of the compressor by resting on a machined woolen cloth at the same time as the upper face of the spacer 62.
- the seal between the suction 60 and discharge 73 collectors, between the discharge collectors 73 and 72, between the discharge 72 and suction 71 collectors is provided respectively by the seals 6 and 7, 67 and 76 all identical.
- the tightness between the valve 63 and the rod 78 is taken into account by the segments 37 preferably executed in fluorocarbon material, housed in grooves machined in the sleeve 64.
- This sleeve threaded at the end at its periphery also ensures the tightening of the two parts constituting the valve 63, the details of which are illustrated in FIG. 5.
- This valve 63 derives closely from the valve 3 by removing the suction 48 and discharge 47 lights (FIG. 1) and replacing the tightening nut 49 by the sleeve. 64.
- Inside the removable jacket 65 slides the working piston 66 fixed to the rod 78 by a concentric screw 79.
- the piston 66 is provided at its periphery with a plurality of sealing segments 84 preferably made of material fluorocarbon.
- the superimposed arrangement of the various suction and discharge collectors allows, by various appropriate connections on the front and rear faces of the compressor (not shown) and by judicious internal partitioning, to simply produce single or two-stage versions of this compressor by being able, moreover, to vary the staging rate according to the position of the internal partitions.
- the "head-to-tail" arrangement of the valves makes it possible to combine the advantages of double effect, with a possibility of power reduction up to 50% of an "anti-liquid" system for one of the aspirations. and the possibility of accommodating large diameter valves reducing pressure losses.
- the invention also makes it possible, if necessary, to provide the lower valve 63 with a “liquid cut-off” device, as shown in FIG.
- a spring 87 identical to the spring 31, bears on the part 64, on the one hand, and on a counterbore machined at the same time as the upper face of the spacer 62, on the other hand.
- the cylindrical lower part of the support piece 69 engages in a corresponding bore in the spacer 62, the seal at this bore being obtained by the seals 88.
- the cable gland 70 is, in turn, held in place by a cover 89 screwed onto the lower part of the part 69.
- this construction allows mounting by stacking inside a single bore of the valve system of the invention as described in FIG. 1, as well as a reuse for the dry piston compressor of a maximum of component parts of the lubricated piston compressor with only slight modifications (valves, bearing parts, movable cylinder head and power reduction devices, seals, lower pistons, cover, etc.).
- the superimposed arrangement of the collectors makes it easy to produce single or multi-stage versions with variable layering rate.
- FIG. 7 An exemplary embodiment of such a dry compressor, starting from standard parts of a basic model of the lubricated type, is illustrated in FIG. 7 where the same construction is found by stacking the pistons, jacket and valves of the dry compressor in the same bore of the cylinder head 83, 61 of FIGS. 4 and 6, but where the latter is replaced by two cylinder heads 51 of lubricated piston compressor of the type described in FIGS. 1 to 3, separated by a spacer 91 receiving the shirts 65, the lower cylinder head 51 then resting on the spacer plate 62 in the inverted position.
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Abstract
Cylinder heads of piston compressors, particularly for refrigerating fluids with center suction valves set on the flange of the liner and bearing elastically against the cylinder head cover, forming "liquid anti-surge valve." The backing with elastical setting of the valve (3) on the liner (2) is achieved by means of an intermediary piece (5) in which a control push rod (30) of a load-shedding valve (4) under the thrust of elastic means (16) put out of action during normal run by a reversal thrust of a servo fluid applied through conduits (9) in a bore provided in the intermediary piece (5) on a piston integral with the push rod (30) against said elastic means (16).
Description
La présente invention, due à la collaboration de M. François LEORAT, se rapporte à l'agencement des culasses de compresseurs à pistons, notamment pour fluide frigorigène et, en particulier, à la commande des dispositifs de réduction de puissance frigorifique pour compresseurs équipés de culasses mobiles "anticoup de liquide" et munis de clapets automatiques à aspiration centrale. The present invention, due to the collaboration of Mr. François LEORAT, relates to the arrangement of the cylinder heads of piston compressors, in particular for refrigerant and, in particular, to the control of the cooling power reduction devices for compressors equipped with movable cylinder heads "against liquid" and fitted with automatic valves with central aspiration.
Dans la plupart des réalisations connues de compresseurs à pistons, la commande du dispositif de réduction de puissance cylindre par cylindre et son alimentation hydraulique ou pneumatique, le mécanisme de culasse mobile, l'étanchéité entre enceintes basse et haute pression, sont conçus de manière fonctionnellement indépendante, ce qui a pour conséquence de multiplier les pièces constitutives. Il en résulte un coût de fabrication élevé et une fiabilité de fonctionnement en raison inverse de la complexité de l'ensemble.In most known embodiments of piston compressors, the control of the cylinder-by-cylinder power reduction device and its hydraulic or pneumatic supply, the movable cylinder head mechanism, the sealing between low and high pressure chambers, are functionally designed. independent, which has the consequence of multiplying the constituent parts. This results in a high manufacturing cost and reliability of operation in inverse ratio to the complexity of the assembly.
L'objet de la présente invention consiste, au contraire, en une construction intégrée conduisant à un nombre minimal de pièces constitutives, ce qui entraîne un montage et des interventions de maintenance très simples, un bas coût de réalisation et une très bonne fiabilité de fonctionnement, ce dernier point revêtant une importance toute particulière dans les applications de froid industriel.The object of the present invention consists, on the contrary, in an integrated construction leading to a minimum number of constituent parts, which results in very simple assembly and maintenance interventions, low cost of production and very good operating reliability. , this last point being of particular importance in industrial refrigeration applications.
Les caractéristiques et les avantages résultant de l'invention ressortiront de la description qui va suivre, en référence aux figures 1 à 7 annexées qui représentent des vues en coupe selon l'axe d'un cylindre, perpendiculairement à l'axe du vilebrequin.
- La figure 1 décrit une réalisation de l'invention compatible avec une culasse mobile ayant pour élément élastique un ressort hélicoïdal.The characteristics and advantages resulting from the invention will emerge from the description which follows, with reference to the appended FIGS. 1 to 7 which represent views in section along the axis of a cylinder, perpendicular to the axis of the crankshaft. - Figure 1 describes an embodiment of the invention compatible with a movable cylinder head having for elastic element a helical spring.
- La figure 2 représente une variante de la réalisation de la figure 1 où la fonction du ressort hélicoïdal est assurée par des rondelles Belleville.- Figure 2 shows a variant of the embodiment of Figure 1 where the function of the coil spring is provided by Belleville washers.
- La figure 3 représente une réalisation de l'invention conduisant à une culasse à mise en pression hydraulique et dispositif de sécurité par pièces à rupture programmée. - La figure 4 montre une application de l'invention à une construction de compresseur dit "à pistons secs".- Figure 3 shows an embodiment of the invention leading to a cylinder head with hydraulic pressurization and safety device by pieces with programmed failure. - Figure 4 shows an application of the invention to a compressor construction called "dry pistons".
- La figure 5 montre une structure de clapet, variante de la construction précédente.- Figure 5 shows a valve structure, variant of the previous construction.
- La figure 6 montre un dispositif "anticoup de liquide" en variante de l'application des figures 4 et 5.- Figure 6 shows an "anti-liquid" device as an alternative to the application of Figures 4 and 5.
- La figure 7 montre une variante du dispositif précédent dans laquelle la culasse du compresseur à pistons secs est formée d'un empilage entretoisé de deux culasses de compresseurs du type lubrifié, la culasse inférieure étant inversée. 'Dans l'exemple de réalisation, illustré par la figure 1, le clapet automatique 3 repose sur la collerette de la chemise 2 du cylindre. Il est maintenu dans cette position par l'intermédiaire de la pièce d'appui 5- Cette pièce peut coulisser verticalement dans l'alésage correspondant de la culasse 51. Les nervures 35 de la pièce d'appui 5 délimitent des passages profilés à travers lesquels circulent des gaz provenant du collecteur 60 lorsque, à l'admission, ils sont aspirés par le piston 1 à. travers les orifices 42 du clapet 3. Les nervures 35 supportent, en partie haute de la pièce d'appui 5, un alésage 33 à l'extérieur duquel prend appui, sur la collerette 37, un ressort hélicoïdal 31. A son extrémité supérieure, le ressort 31 repose sur une couronne plane d'appui, usinée dans une réalisation préférentielle de l'invention, en même temps que le plan de joint du couvercle de culasse 19. A l'intérieur du cylindre33 coulisse un piston 30 dont la tige vient appuyer, en position basse, sur le dispositif de réduction de puissance 4 connu en soi. Ce dispositif repousse la plaque de fermeture 44 du clapet 3 par l'intermédiaire des pattes 41, ce qui empêche l'obturation des
orifices d'admission 42 durant la phase de compression ; dans ces conditions, au lieu que le fluide frigorigène soit comprimé et refoulé dans le collecteur d'échappement 50 à travers les orifices 46, le fluide reflue dans l'enceinte d'admission. Le piston 30 est alimenté en fluide de servitude, distribué par exemple par une électrovanne non représentée, par le canal 34 situé dans la culasse 51, puis par le canal 9 percé dans l'épaisseur de l'une des nervures 35 et qui débouche dans la rainure 8 usinée à la périphérie de la pièce d'appui 5. L'étanchéité entre la culasse 51 et la pièce d'appui 5 est assurée par les deux joints 6 et 7 qui réalisent simultanément l'étanchéité du circuit d'alimentation du piston 30 et l'étanchéité entre les enceintes d'admission 60 et de refoulement 50 du fluide de travail.- Figure 7 shows a variant of the previous device in which the cylinder head of the dry piston compressor is formed from a braced stack of two compressor cylinder heads of the lubricated type, the lower cylinder head being inverted. 'In the embodiment, illustrated in Figure 1, the automatic valve 3 rests on the collar of the jacket 2 of the cylinder. It is held in this position by means of the support piece 5- This piece can slide vertically in the corresponding bore of the cylinder head 51. The ribs 35 of the support piece 5 delimit profiled passages through which gases from the manifold 60 circulate when, on admission, they are sucked by the piston 1 to. through the orifices 42 of the valve 3. The ribs 35 support, in the upper part of the support piece 5, a bore 33 outside of which bears, on the flange 37, a helical spring 31. At its upper end, the spring 31 rests on a flat bearing ring, machined in a preferred embodiment of the invention, at the same time as the joint plane of the cylinder head cover 19. Inside the cylinder33 slides a piston 30, the rod of which comes press, in the low position, on the power reduction device 4 known per se. This device pushes the closure plate 44 of the valve 3 through the legs 41, which prevents the obturation of the intake ports 42 during the compression phase; under these conditions, instead of the refrigerant being compressed and discharged into the exhaust manifold 50 through the orifices 46, the fluid flows back into the intake enclosure. The piston 30 is supplied with service fluid, distributed for example by a solenoid valve not shown, by the channel 34 located in the cylinder head 51, then by the channel 9 pierced in the thickness of one of the ribs 35 and which opens into the groove 8 machined at the periphery of the support piece 5. The seal between the cylinder head 51 and the support piece 5 is provided by the two seals 6 and 7 which simultaneously seal the supply circuit of the piston 30 and the seal between the inlet 60 and discharge 50 enclosures of the working fluid.
En position haute, le piston 30 libère, par conséquent, le dispositif de réduction de puissance 4 et vient en butée sur le circlips 32 tout en comprimant le ressort de rappel 16.In the high position, the piston 30 releases, therefore, the power reduction device 4 and comes into abutment on the circlip 32 while compressing the return spring 16.
Il en résulte que si le fluide de servitude est l'huile de graissage du compresseur, le démarrage de ce dernier s'effectue, faute d'une pression d'huile immédiatement suffisante pour repousser le piston 30, automatiquement en charge nulle.It follows that if the service fluid is the lubricating oil of the compressor, the start-up of the latter takes place, in the absence of an oil pressure immediately sufficient to push the piston 30, automatically at zero load.
En cas de "coup d'huile" ou de "liquide" - afflux intempestif d'huile de lubrification ou de fluide de travail condensé dans le cylindre du compresseur - le clapet de refoulement 45 est, en général, incapable de livrer un passage suffisamment rapide au liquide comprimé par le piston 1 si bien qu'il se produit une surpression instantanée telle que la tare en place du ressort 31, calculée pour assurer l'immobilisation du clapet 3 en marche normale, est insuffisante pour maintenir en place le clapet 3. Ce dernier se soulève alors, entraînant avec lui la pièce 5 qui coulisse dans la culasse et livre passage au liquide entre lui-même et la collerette de la chemise 2. Sous l'effet du ressort 31, l'ensemble clapet 3 - pièce d'appui 5 reprend sa position de service normale dès que l'afflux de liquide est éliminé.In the event of an "oil spill" or "liquid" - untimely flow of lubricating oil or condensed working fluid into the compressor cylinder - the discharge valve 45 is, in general, incapable of delivering sufficient passage fast to the liquid compressed by the piston 1 so that an instantaneous overpressure occurs such that the tare in place of the spring 31, calculated to ensure the immobilization of the valve 3 in normal operation, is insufficient to keep the valve 3 in place The latter is then raised, carrying with it the part 5 which slides in the cylinder head and delivers passage to the liquid between itself and the collar of the shirt 2. Under the effect of the spring 31, the valve 3 assembly - part support 5 returns to its normal operating position as soon as the flow of liquid is eliminated.
On constate donc que, selon l'invention, la seule pièce d'appui 5 remplit simultanément les fonctions de :It can therefore be seen that, according to the invention, the single support piece 5 simultaneously fulfills the functions of:
- transmission de l'effort du ressort 31 au clapet 3, assurant maintien en place de ce dernier,
- guidage du piston de commande 30 du dispositif de réduction de puissance,- transmission of the force of the spring 31 to the valve 3, ensuring that the latter is held in place, - guiding the control piston 30 of the power reduction device,
- alimentation en fluide de travail du piston de commande 30,- supply of working fluid to the control piston 30,
- étanchéité simultanée du circuit d'alimentation du piston 30 et entre les enceintes haute et basse pression du compresseur.- simultaneous sealing of the piston 30 supply circuit and between the high and low pressure chambers of the compressor.
On constate également que, selon un mode de réalisation préférentiel, l'invention se combine avantageusement avec un surfaçage simultané du plan de joint du couvercle 19 de culasse et des couronnes d'appui sur le couvercle 19 des ressorts 31 et 16. Il en résulte que la longueur en place de ces ressorts peut être contrôlée avec beaucoup de précision sans aucun surcoût de fabrication. La dispersion sur les tares en place est, par voie de conséquence, réduite à un minimum. Cet avantage est encore plus déterminant lorsque, pour des considérations d'encombrement en hauteur, il est souhaitable de substituer au ressort hélicoïdal 31 des diaphragmes Belleville 36 en parallèle (cette variante de réalisation de l'invention est illustrée par la figure 2) ; en effet, ce montage exige une excellente précision pour le positionnement des diaphragmes pour s'assurer, en particulier, que le taux de contraintes reste acceptable sur toute la longueur de la course.It is also noted that, according to a preferred embodiment, the invention is advantageously combined with a simultaneous surfacing of the joint plane of the cover 19 of the cylinder head and of the bearing rings on the cover 19 of the springs 31 and 16. This results in that the length in place of these springs can be controlled with great precision without any additional manufacturing cost. The dispersion on the tares in place is, consequently, reduced to a minimum. This advantage is even more decisive when, for considerations of overall height, it is desirable to replace the helical spring 31 of the Belleville diaphragms 36 in parallel (this variant embodiment of the invention is illustrated in FIG. 2); indeed, this assembly requires excellent precision for the positioning of the diaphragms to ensure, in particular, that the stress rate remains acceptable over the entire length of the stroke.
Enfin, comme on va le voir à l'occasion de la description du montage illustré par la figure 3, le principe de l'invention s'applique de manière non limitative aux culasses mobiles anticoup de liquide du type à pièce de rupture programmée. On sait que ce type de culasse trouve sa justification dans le fait que l'élément élastique - ressort hélicoïdal ou diaphragmes Belleville - maintenant en place le clapet automatique peut voir ses caractéristiques mécaniques se dégrader dans le temps au point que le clapet en vient à battre sur la collerette 2 pour certains régimes de marche, ce qui entraîne des bruits de fonctionnement et une détérioration des portées. Par ailleurs, en dehors même de toute dégradation des caractéristiques mécaniques de l'élément élastique, il arrive que lors d'un "coup de liquide" une impureté vienne s'interposer à la retombr'e du clapet 3 entre ce dernier et la collerette 2, ce qui entraîne une perte d'étanchéité très préjudiciable au rendement du compresseur. C'est pour ces raisons que, dais certains cas, on est amené à admettre que tout coup de liquide d'une intensité suffisante
entraîne la rupture d'une pièce de sécurité prévue à cet effet : l'arrêt du compresseur est alors obligatoire pour procéder à l'inspection du clapet 3, à son repositionnement parfait sur la collerette 2 et au remplacement de la pièce de sécurité rompue. La figure 3 montre comment l'invention peut s'appliquer directement au concept de culasse à pièce de rupture. La pièce d'appui 5 conserve la même morphologie générale que dans les figures 1 et 2, mais le diamètre du cylindre 33 est augmenté autant qu'il le faut pour disposer d'une force d'appui du clapet 3 sur la collerette 2 suffisanté pour tous les régimes de marche. Le piston 11 qui se meut à l'intérieur du cylindre 33 coulisse librement sur la tige 10. L'extrémité inférieure de cette tige appuie, en position basse, sur le dispositif de réduction de puissance 4, tandis qu'à son extrémité supérieure filetée elle est fixée par le boulon 17 au fond de la pièce 18. La pièce 18 présente un évidement cylindrique qui sert de logement au ressort 16 qui s'appuie sur une couronne plane 21 usinée en même temps dans une réalisation préférentielle que le plan de joint du couvercle de culasse 19. La pièce 18 présente un certain nombre de bras rayonnants 22 qui aboutissent à une couronne circulaire 14 qui s'appuie, par l'intermédiaire de plots 23, sur la face supérieure du piston 11. Les bras 22 présentent en leur milieu une section affaiblie 15 calculée de manière à se rompre sous un effort précalculé comme limite supérieure de la poussée admissible par les organes du compresseur dont elle sera la première pièce à se rompre au-delà de cette poussée permettant, en outre, son délestage comme dans les exemples précédemment décrits.Finally, as will be seen on the occasion of the description of the assembly illustrated in FIG. 3, the principle of the invention applies in a nonlimiting manner to movable cylinder heads against liquid blow of the type with programmed rupture part. We know that this type of cylinder head finds its justification in the fact that the elastic element - helical spring or Belleville diaphragms - now in place the automatic valve can see its mechanical characteristics deteriorate over time to the point that the valve comes to beat on the flange 2 for certain operating speeds, which causes operating noise and deterioration of the ranges. Furthermore, even without any degradation of the mechanical characteristics of the elastic element, it happens that during a "liquid blow" an impurity comes to intervene in the retombr'e of the valve 3 between the latter and the flange 2, which results in a loss of tightness very detrimental to the performance of the compressor. It is for these reasons that, in some cases, we are led to admit that any stroke of liquid of sufficient intensity leads to the rupture of a safety part provided for this purpose: stopping the compressor is then compulsory in order to inspect the valve 3, to reposition it perfectly on the flange 2 and to replace the broken security part. FIG. 3 shows how the invention can be applied directly to the concept of cylinder head with rupture part. The support piece 5 retains the same general morphology as in FIGS. 1 and 2, but the diameter of the cylinder 33 is increased as much as is necessary to have a support force of the valve 3 on the flange 2 sufficient for all walking regimes. The piston 11 which moves inside the cylinder 33 slides freely on the rod 10. The lower end of this rod presses, in the low position, on the power reduction device 4, while at its upper threaded end it is fixed by the bolt 17 to the bottom of the part 18. The part 18 has a cylindrical recess which serves as a housing for the spring 16 which rests on a flat crown 21 machined at the same time in a preferred embodiment than the joint plane of the cylinder head cover 19. The part 18 has a certain number of radiating arms 22 which lead to a circular crown 14 which rests, by means of studs 23, on the upper face of the piston 11. The arms 22 have in their middle a weakened section 15 calculated so as to rupture under a precomputed force as upper limit of the admissible thrust by the organs of the compressor of which it will be the first part to rupture beyond this thrust allowing, in addition, its load shedding as in the examples previously described.
Lorsque le piston 11 n'est pas alimenté en fluide de travail, le ressort 16 maintient en position basse l'ensemble piston 11, pièce 18, tige 10 et le dispositif de réduction de puissance 4 est actionné. Le ressort 16 est calculé de manière que, dans la position décrite ci-dessus, le clapet 3 soit maintenu sans battements sur la collerette 2 lorsque le compresseur tourne à vide. Lorsque le piston 11 est alimenté en fluide de travail, l'ensemble piston 11, tige 10, pièce 18 se met en position haute, la pièce 18 venant en appui sur la couronne 21 ; le dispositif de réduction de puissance 4 est alors libéré et le délestage supprimé. En cas de coup de liquide, l'ensemble clapet 3 - pièce 5 a
tendance à se soulever. Si le coup de liquide est de faible intensité, il se peut que l'élasticité du fluide de travail enfermé entre le cylindre 33 et le piston ainsi que le volume de fluide refoulé par les conduits 9 et 34 permettent une levée suffisante du clapet 3. Dans le cas contraire, l'effort transmis est tel que les bras 22 se rompent au niveau des sections affaiblies 15. Le piston 11 vient alors en butée sur la couronne 21 par l'intermédiaire de plots 23 ; la pièce 18, désolidarisée du piston 11, descend sous l'effort du ressort 16 et, par l'intermédiaire de la tige 10, actionne le dispositif 4 de réduction de puissance ; ainsi en cas de coup de liquide, le cylindre concerné du compresseur est automatiquement mis à la décharge après rupture de la pièce de sécurité au niveau des sections 22. Par ailleurs, la géométrie de la pièce 18 est telle que, même après rupture, les deux tronçons restent maintenus en place et ne peuvent aller causer d'avaries dans une autre partie du compresseur.When the piston 11 is not supplied with working fluid, the spring 16 maintains the piston 11, part 18, rod 10 assembly in the low position and the power reduction device 4 is actuated. The spring 16 is calculated so that, in the position described above, the valve 3 is held without beating on the flange 2 when the compressor is running empty. When the piston 11 is supplied with working fluid, the piston 11, rod 10, part 18 assembly moves to the high position, the part 18 coming to bear on the crown 21; the power reduction device 4 is then released and the load shedding removed. In the event of a liquid blow, the valve 3 - part 5 a assembly tendency to lift. If the liquid blow is of low intensity, it may be that the elasticity of the working fluid enclosed between the cylinder 33 and the piston as well as the volume of fluid discharged through the conduits 9 and 34 allow a sufficient lifting of the valve 3. Otherwise, the force transmitted is such that the arms 22 break at the weakened sections 15. The piston 11 then comes into abutment on the crown 21 by means of studs 23; the part 18, detached from the piston 11, descends under the force of the spring 16 and, by means of the rod 10, actuates the device 4 for reducing power; thus in the event of a liquid blow, the cylinder concerned of the compressor is automatically put to discharge after rupture of the safety part at the level of sections 22. Furthermore, the geometry of part 18 is such that, even after rupture, the two sections remain held in place and cannot cause damage to another part of the compressor.
Ainsi, la culasse mobile "anticoup de liquide" pour clapet à aspiration centrale, selon l'invention, est caractérisée par une pièce unique, la pièce intermédiaire 5, qui assure la transmission de l'effort d'appui du ressort principal de rappel (hélicoïdal ou Belleville), le guidage du piston de commande de la réduction de puissance et l'alimentation dudit piston de commande.Thus, the movable "liquid blow" cylinder head for a central suction valve, according to the invention, is characterized by a single piece, the intermediate piece 5, which transmits the bearing force of the main return spring ( helical or Belleville), guiding the power reduction control piston and supplying said control piston.
Les joints d'étanchéité du circuit alimentant le piston de commande assurent simultanément l'étanchéité entre enceintes haute et basse pression du compresseur.The seals of the circuit supplying the control piston simultaneously seal the high and low pressure chambers of the compressor.
Le compresseur démarre automatiquement à charge nulle si le fluide de servitude est l'huile de graissage du compresseur dont la mise en pression fera alors relâcher le clapet de délestage.The compressor starts automatically at zero load if the service fluid is the lubricating oil of the compressor whose pressurization will then release the load-shedding valve.
Dans sa forme la plus générale, le perfectionnement aux culasses de compresseurs à pistons à clapet à aspiration centrale calé sur la collerette de chemise en appui élastique contre le couvercle de culasse en configuration dite "anticoup de liquide" selon l'invention est caractérisé en ce que l'appui par calage élastique du clapet 3 sur la chemise 2 est réalisé au moyen d'une pièce intermédiaire 5 dont les surfaces de contact sur la culasse 51 et sur le clapet 3 forment une séparation étanche 35 des enceintes à haute et basse pression du compresseur.
Suivant une forme de réalisation préférée, ce perfectionnement aux culasses de compresseur à pistons à clapet à aspiration centrale calé sur la collerette de chemise en appui élastique contre le couvercle de culasse en configuration dite "anticoup de liquide" se caractérise en ce que l'appui à calage élastique du clapet 3 sur la chemise 2 est réalisé par une pièce intermédiaire 5 dans laquelle est disposé un poussoir(30, 10)de commande d'un dispositif de délestage 4, 41, 43, 44.mis en action par la poussée de moyens élastiques 16, mis hors service en marche normale par une poussée inverse d'un fluide de servitude amené par des conduits 9, 34 dans un alésage aménagé dans la pièce intermédiaire 5, poussée s'exerçant sur un piston solidaire du poussoir 30, 10 contre lesdits moyens élastiques 16.In its most general form, the improvement to the cylinder heads of reciprocating piston compressors with central aspiration wedged on the sleeve flange in elastic abutment against the cylinder head cover in the configuration known as "liquid shock" according to the invention is characterized in that that the support by elastic wedging of the valve 3 on the liner 2 is produced by means of an intermediate piece 5 whose contact surfaces on the cylinder head 51 and on the valve 3 form a sealed separation 35 from the high and low pressure chambers compressor. According to a preferred embodiment, this improvement to the compressor compressor piston heads with central suction valve wedged on the sleeve flange in elastic support against the cylinder head cover in the so-called "liquid shock" configuration is characterized in that the support with elastic setting of the valve 3 on the liner 2 is produced by an intermediate piece 5 in which is arranged a pusher (30, 10) for controlling a load shedding device 4, 41, 43, 44. actuated by the thrust elastic means 16, put out of service in normal operation by a reverse thrust of a service fluid supplied by conduits 9, 34 into a bore arranged in the intermediate part 5, thrust being exerted on a piston secured to the plunger 30, 10 against said elastic means 16.
La pièce intermédiaire 5 coulisse en préservant l'étanchéité 6, 7 entre les enceintes basse et haute pression du compresseur dans un alésage de la culasse 51 recevant également le clapet à aspiration centrale 3.The intermediate part 5 slides while preserving the seal 6, 7 between the low and high pressure chambers of the compressor in a bore of the cylinder head 51 also receiving the central suction valve 3.
L'étanchéité de coulissement de la pièce intermédiaire 5 est assurée par au moins deux joints 6, 7 entre lesquels une gorge circulaire 8 communique avec un conduit 34 de la culasse 51 amenant le fluide de servitude sous pression et avec un conduit 9 de la pièce intermédiaire 5 amenant ce fluide dans l'alésage du piston solidaire du poussoir de commande 30.The sliding seal of the intermediate piece 5 is ensured by at least two seals 6, 7 between which a circular groove 8 communicates with a pipe 34 of the cylinder head 51 bringing the service fluid under pressure and with a pipe 9 of the piece intermediate 5 bringing this fluid into the bore of the piston integral with the control pusher 30.
Les couronnes d'appui sur le couvercle de culasse des moyens élastiques 16, 31, agissant sur le poussoir 30 et la pièce intermédiaire 5, sont avantageusement usinées par le même dressage plan que celui de la surface d'appui du couvercle 19, 62 de la culasse 51.The bearing rings on the cylinder head cover of the elastic means 16, 31, acting on the pusher 30 and the intermediate piece 5, are advantageously machined by the same plane dressing as that of the bearing surface of the cover 19, 62 of cylinder head 51.
Le dispositif permet d'utiliser, avec une bonne précision de poussée, comme moyens élastiques de poussée mettant en appui la pièce intermédiaire 5, un empilage de rondelles Belleville 36 montées entre des plans parallèles usinés.The device makes it possible to use, with good thrust precision, as elastic thrust means bearing on the intermediate part 5, a stack of Belleville washers 36 mounted between machined parallel planes.
En variante, l'appui élastique de la pièce intermédiaire 5 contre le couvercle 19 réalisant le calage du clapet 3 sur la chemise 2 peut être assuré par la pression du fluide de servitude assurant également le retrait du poussoir actionnant le dispositif de délestage 10 par l'intermédiaire d'une pièce de rupture 23, 15, 22, 18 en appui direct sur le couvercle 19.
Enfin, le dispositif s'applique particulièrement à la culasse d'un compresseur sec à double effet dans lequel la chemise 65 est fermée par deux pièces d'appui 5, 69, l'ensemble étant empilé dans un même alésage d'une culasse 61, 83 et mis en appui sur une entretoise-couvercle 62 recouvrant le bloc des pistons 81 d'un modèle de compresseur de base lubrifié, auxquels sont attelés les pistons secs 66 par des tiges 78 coulissant de façon étanche à travers les pièces intermédiaires 69 et les clapets inférieurs 63. La pièce intermédiaire inférieure 69 est alors usinée pour recevoir un dispositif d'étanchéité 70 de passage de la tige 78 de liaison des pistons 66, 81 en lieu et place du système de commande du poussoir de délestage 30.Alternatively, the elastic support of the intermediate piece 5 against the cover 19 realizing the setting of the valve 3 on the jacket 2 can be ensured by the pressure of the service fluid also ensuring the withdrawal of the pusher actuating the load shedding device 10 by l 'through a rupture part 23, 15, 22, 18 in direct support on the cover 19. Finally, the device is particularly applicable to the cylinder head of a dry double-acting compressor in which the jacket 65 is closed by two support parts 5, 69, the assembly being stacked in the same bore of a cylinder head 61 , 83 and supported on a cover-spacer 62 covering the piston block 81 of a basic lubricated compressor model, to which the dry pistons 66 are coupled by rods 78 sliding in leaktight manner through the intermediate parts 69 and the lower valves 63. The lower intermediate part 69 is then machined to receive a sealing device 70 for passage of the rod 78 connecting the pistons 66, 81 in place of the control system for the load shedding pusher 30.
Cette pièce intermédiaire inférieure 69 pourra être en appui étanche 75 sur une surface usinée de l'entretoise-couvercle 62 ou coulissée de façon étanche 88 dans un alésage du couvercle-entretoise 62 en cas de soulèvement accidentel du clapet inférieur 63 contre un moyen élastique 87, le compresseur sec étant ainsi muni, dans les deux sens, d'un clapet "anticoup de liquide", la chemise 65 étant alors bloquée en translation par un goujon engagé dans une gorge 90 dans son alésage de la culasse 61.This lower intermediate piece 69 may be in leaktight support 75 on a machined surface of the spacer-cover 62 or slidably sealed 88 in a bore of the spacer-cover 62 in the event of accidental lifting of the lower valve 63 against an elastic means 87 , the dry compressor being thus provided, in both directions, with a "liquid blow" valve, the jacket 65 then being blocked in translation by a stud engaged in a groove 90 in its bore of the cylinder head 61.
Le clapet inférieur 63 aura ses deux plaques 92, 93 assemblées par une douille filetée centrale 64 dont l'alésage intérieur central où coulisse la tige de liaison des pistons 78 est muni de joints d'étanchéité 87. Enfin, la culasse 61, 83 du compresseur sec sera avantageusement formée de deux culasses 51 de compresseurs du type à pistons lubrifiés, empilées et séparées par une entretoise 91 recevant les chemises 65, la culasse 51 inférieure reposant en position inversée sur la plaque entretoise-couvercle 62 du bloc de base. Plus généralement, ce perfectionnement s'appliquera aux culasses de compresseurs à double effet construites sur une base de compresseur à simple effet caractérisées en ce que la culasse du compresseur double effet est constituée de deux culεsses 51 du compresseur simple effet 1 empilées et séparées par une entretoise 91 recevant les chemises 65 des cylindres double effet, la culasse 51 inférieure reposant en position inversée sur une plaque entretoisecouvercle 62 du bloc de base.The lower valve 63 will have its two plates 92, 93 assembled by a central threaded sleeve 64 whose central internal bore where the piston connecting rod 78 slides is provided with seals 87. Finally, the cylinder head 61, 83 of the dry compressor will advantageously be formed by two cylinder heads 51 of compressors of the lubricated piston type, stacked and separated by a spacer 91 receiving the liners 65, the lower cylinder head 51 resting in the inverted position on the spacer-cover plate 62 of the base block. More generally, this improvement will apply to double-acting compressor heads built on a single-acting compressor base, characterized in that the double-acting compressor head consists of two single-acting compressor heads 51 stacked and separated by a spacer 91 receiving the sleeves 65 of the double-acting cylinders, the lower cylinder head 51 resting in the inverted position on a spacer-cover plate 62 of the base block.
Cette application de l'invention en particulier aux compres
seurs du type dit "à pistons secs" permet une réduction notable du coût de construction grâce au réemploi de pièces utilisées pour la réalisation de compresseurs à pistons lubrifiés, d'alésage identique ou voisin. La figure 4 qui représente une coupe selon l'axe d'un cylindre, perpendiculairement à l ' axe de rotation du vilebrequin, illustre une réalisation de l'invention appliquée à un compresseur à pistons secs, à double effet, prenant pour base un compresseur à pistons lubrifiés du type vu précédemment et avantageusement issu d'un moteur thermique tel que décrit dans le brevet français n° 77/30663.This application of the invention in particular to compres Sisters of the so-called "dry piston" type allow a significant reduction in the construction cost thanks to the reuse of parts used for the production of compressors with lubricated pistons, of identical or similar bore. Figure 4 which shows a section along the axis of a cylinder, perpendicular to the axis of rotation of the crankshaft, illustrates an embodiment of the invention applied to a dry piston compressor, double acting, based on a compressor with lubricated pistons of the type seen above and advantageously from a heat engine as described in French patent n ° 77/30663.
L'invention s'appliquerait également, sans modifications autres que celles relevant du domaine courant de l'homme de l'art, à tout type de compresseur disposant d'une culasse démontable. En prenant pour base un compresseur à pistons lubrifiés tel que décrit dans le brevet français précité, on remplace la culasse spécifique de ce compresseur par une entretoise 62 fixée en lieu et place par les boulons 74 et qui maintient en place la chemise amovible 2. Une tige 78 est vissée dans le piston 81 et bloquée en rotation par le contre-écrou 80. L'entretoise 62 comporte, au niveau de chaque cylindre, des ouvertures 77 permettant un libre passage des gaz lors des mouvements de translation des pistons 81. L'entretoise 62, prenant appui sur l'encadrement 84 de l'ouverture supérieure de l'enceinte étanche 85, supporte la culasse 61 spécifique au compresseur à pistons secs à double effet, les boulons 82 assujettis sont simultanément la culasse 61 et l'entretoise 62 à l'encadrement 84. Au niveau de chaque cylindre, la culasse 61 présente un alésage 86 dans lequel viennent se loger, en énumérant de bas en haut : une pièce d'appui 69, un clapet automatique 63, une chemise amovible 65 formant entretoise, un clapet automatique 3, une pièce d'appui 5, cet empilage Ηant maintenu en place par le ressort 31 qui prend appui sur le couvercle 19. On notera que la pièce d'appui 69 ne diffère de la pièce d'appui 5 que par l'alésage intérieur qui sert de logement, dans le cas de la pièce 69, au presse-étoupe 70 assurant l'étanchéité au niveau de la tige 78 et par la présence, à sa partie supérieure, des gorges contenant les joints 75 qui réalisent l'étanchéité entre le collecteur d'aspiration 71 et la partie basse du
compresseur en prenant appui sur un lainage usiné en même temps que la face supérieure de l'entretoise 62. Au niveau de l'alésage 86, l'étanchéité entre les collecteurs d'aspiration 60 et de refoulement 73, entre les collecteurs de refoulement 73 et 72, entre les collecteurs de refoulement 72 et d'aspiration 71 est assurée respectivement par les joints 6 et 7, 67 et 76 tous identiques. L'étanchéité entre le clapet 63 et la tige 78 est prise en compte par les segments 37 exécutés préférentiellement en matériau fluorocarboné, logés dans des gorges usinées dans le manchon 64. Ce manchon fileté en extrémité à sa périphérie assure également le serrage des deux parties constitutives du clapet 63 dont le détail est illustré par la figure 5. Ce clapet 63 dérive étroitement du clapet 3 par suppression des lumières d'aspiration 48 et de refoulement 47 (figure 1) et remplacement de l'écrou de serrage 49 par le manchon 64. A l'intérieur de la chemise amovible 65 coulisse le piston de travail 66 fixé à la tige 78 par ia vis concentrique 79. Le piston 66 est muni à sa périphérie d'une pluralité de segments d'étanchéité 84 exécutés préférentiellement en matériau fluorocarboné.The invention would also apply, without modifications other than those relating to the common field of those skilled in the art, to any type of compressor having a removable cylinder head. Taking as a base a compressor with lubricated pistons as described in the aforementioned French patent, the specific cylinder head of this compressor is replaced by a spacer 62 fixed in place of the bolts 74 and which keeps the removable jacket in place 2. A rod 78 is screwed into the piston 81 and locked in rotation by the lock nut 80. The spacer 62 has, at each cylinder, openings 77 allowing free passage of the gases during the translational movements of the pistons 81. L 'spacer 62, bearing on the frame 84 of the upper opening of the sealed enclosure 85, supports the cylinder head 61 specific to the double-acting dry piston compressor, the bolts 82 subject are simultaneously the cylinder head 61 and the spacer 62 at the frame 84. At each cylinder, the cylinder head 61 has a bore 86 in which are housed, listing from bottom to top: a support piece 69, an automatic valve 63, u ne removable jacket 65 forming a spacer, an automatic valve 3, a support piece 5, this Ηant stack kept in place by the spring 31 which bears on the cover 19. It will be noted that the support piece 69 does not differ from the support part 5 only by the internal bore which serves as housing, in the case of part 69, to the stuffing box 70 ensuring sealing at the level of the rod 78 and by the presence, at its upper part, of the grooves containing the seals 75 which seal between the suction manifold 71 and the lower part of the compressor by resting on a machined woolen cloth at the same time as the upper face of the spacer 62. At the bore 86, the seal between the suction 60 and discharge 73 collectors, between the discharge collectors 73 and 72, between the discharge 72 and suction 71 collectors is provided respectively by the seals 6 and 7, 67 and 76 all identical. The tightness between the valve 63 and the rod 78 is taken into account by the segments 37 preferably executed in fluorocarbon material, housed in grooves machined in the sleeve 64. This sleeve threaded at the end at its periphery also ensures the tightening of the two parts constituting the valve 63, the details of which are illustrated in FIG. 5. This valve 63 derives closely from the valve 3 by removing the suction 48 and discharge 47 lights (FIG. 1) and replacing the tightening nut 49 by the sleeve. 64. Inside the removable jacket 65 slides the working piston 66 fixed to the rod 78 by a concentric screw 79. The piston 66 is provided at its periphery with a plurality of sealing segments 84 preferably made of material fluorocarbon.
On notera que la disposition superposée des différents collecteurs d'aspiration et de refoulement permet, par diverses connexions appropriées sur les faces avant et arrière du compresseur (non représentées) et par un cloisonnement interne judicieux, de réaliser simplement des versions mono ou biétagées de ce compresseur en pouvant, de plus, faire varier le taux d'étagement selon la position des cloisonnements internes. De plus, l'agencement "tête-bêche" des clapets permet de cumuler les avantages de double effet, d'une possibilité de réduction de puissance jusqu'à 50 % d'un système "anticoup de liquide" pour l'une des aspirations et de la possibilité de loger des clapets de grand diamètre réduisant les pertes de charge. On peut enfin noter que l'invention permet également, si cela s'avère nécessaire, de doter le clapet inférieur 63 d'un dispositif "anticoup de liquide", comme le montre la figure 6 ; un ressort 87, identique au ressort 31, prend appui sur la pièce 64, d'une part, et sur un lamage usiné en même temps que la face supérieure de l'entretoise 62, d'autre part. La partie inférieure cylindrique de la pièce d'appui 69 s'engage dans un alésage correspondant de l'entretoise 62, l'étanchéité au niveau de cet alésage étant obtenue par les joints 88.
Le presse-étoupe 70 est, quant à lui, maintenu en place par un couvercle 89 vissé surla partie inférieure de la pièce 69. Afin d'assurer un positionnement rigoureux de la chemise 65 soumise aux efforts différentiels des ressorts 31 et 87, une clavette non représentée d'axe horizontal et orthogonal à l'axe du vilebrequin vjont bloquer tangentiellement deux chemises 65 contiguës en pénétrant dans une gorge 90 usinée entre les gorges recevant les joints 67.It will be noted that the superimposed arrangement of the various suction and discharge collectors allows, by various appropriate connections on the front and rear faces of the compressor (not shown) and by judicious internal partitioning, to simply produce single or two-stage versions of this compressor by being able, moreover, to vary the staging rate according to the position of the internal partitions. In addition, the "head-to-tail" arrangement of the valves makes it possible to combine the advantages of double effect, with a possibility of power reduction up to 50% of an "anti-liquid" system for one of the aspirations. and the possibility of accommodating large diameter valves reducing pressure losses. Finally, it can be noted that the invention also makes it possible, if necessary, to provide the lower valve 63 with a “liquid cut-off” device, as shown in FIG. 6; a spring 87, identical to the spring 31, bears on the part 64, on the one hand, and on a counterbore machined at the same time as the upper face of the spacer 62, on the other hand. The cylindrical lower part of the support piece 69 engages in a corresponding bore in the spacer 62, the seal at this bore being obtained by the seals 88. The cable gland 70 is, in turn, held in place by a cover 89 screwed onto the lower part of the part 69. In order to ensure a rigorous positioning of the jacket 65 subjected to the differential forces of the springs 31 and 87, a key not shown with a horizontal axis and orthogonal to the axis of the crankshaft vjont tangentially block two adjoining sleeves 65 by entering a groove 90 machined between the grooves receiving the seals 67.
Ainsi, cette construction permet un montage par empilement à l'intérieur d'un alésage unique du système de clapet de l'invention telle que décrite à la figure 1, ainsi qu'une réutilisation pour le compresseur à pistons secs d'un maximum de pièces constitutives du compresseur à pistons lubrifiés avec seulement de légères modifications (clapets, pièces d'appuis, dispositifs de culasse mobile et de réduction de puissance, joints d'étanchéité, pistons inférieurs, couvercle, etc.). Enfin, la disposition superposée des collecteurs permet de réaliser aisément des versions mono ou multi-étage à taux d' étagement variable.Thus, this construction allows mounting by stacking inside a single bore of the valve system of the invention as described in FIG. 1, as well as a reuse for the dry piston compressor of a maximum of component parts of the lubricated piston compressor with only slight modifications (valves, bearing parts, movable cylinder head and power reduction devices, seals, lower pistons, cover, etc.). Finally, the superimposed arrangement of the collectors makes it easy to produce single or multi-stage versions with variable layering rate.
Un exemple de réalisation d'un tel compresseur sec, à partir de pièces de série d'un modèle de base du type lubrifié, est illustré sur la figure 7 où l'on retrouve la même construction par empilage des pistons, chemise et clapets du compresseur sec dans un même alésage de la culasse 83, 61 des figures 4 et 6, mais où celle-ci est remplacée par deux culasses 51 de compresseur à pistons lubrifiés du type décrit aux figures 1 à 3, séparées par une entretoise 91 recevant les chemises 65, la culasse 51 inférieure reposant alors sur la plaque entretoise 62 en position inversée.An exemplary embodiment of such a dry compressor, starting from standard parts of a basic model of the lubricated type, is illustrated in FIG. 7 where the same construction is found by stacking the pistons, jacket and valves of the dry compressor in the same bore of the cylinder head 83, 61 of FIGS. 4 and 6, but where the latter is replaced by two cylinder heads 51 of lubricated piston compressor of the type described in FIGS. 1 to 3, separated by a spacer 91 receiving the shirts 65, the lower cylinder head 51 then resting on the spacer plate 62 in the inverted position.
Dans une telle construction, seules les plaques entretoises 62 et 91, pièces venues dé fonderie ou mécanosoudées relativement simples, ne sont pas des pièces de série standard du compresseur de base qui, en dehors de sa culasse et de ses clapets, peut, par ailleurs, emprunter ses autrer organes aux éléments de moteurs thermiques alternatifs construits en grandes séries suivant la technique décrite dans la demande de brevet français n° 77/30 663 précitée ; il en résulte donc une construction de compresseurs secs particulièrement économique.
In such a construction, only the spacer plates 62 and 91, parts from the foundry or relatively simple mechanically welded, are not standard series parts of the basic compressor which, apart from its cylinder head and its valves, can, moreover , borrow its other organs from the elements of reciprocating heat engines built in large series according to the technique described in the French patent application n ° 77/30 663 mentioned above; this therefore results in a particularly economical construction of dry compressors.
Claims
REVENDICATIONS
1 - Perfectionnement aux culasses de compresseurs à pistons à clapet à aspiration centrale calé sur la collerette de chemise en appui élastique contre le couvercle de la culasse en configuration dite "anticoup de liquide" comportant un appui par calage élastique du clapet (3) sur la chemise (2) réalisé au moyen d'une pièce intermédiaire (5) dont les surfaces de contact sur la culasse (51) et sur le clapet (3) forment une séparation étanche (35) des enceintes à haute et basse pression du compresseur, l'étanchéité du coulissement de la pièce intermédiaire (5) étant assurée par au moins deux joints (6, 7) entre lesquels une gorge circulaire (β) communique avec un conduit (34) aménagé dans la culasse (51 ) amenant un fluide de servitude sous pression caractérisé en ce que l'appui par calage élastique du clapet (3) sur la chemise (2) est réalisé au moyen de la pièce intermédiaire (5) dans laquelle est disposé un poussoir (30, 10) de commande d'un dispositif de délestage (4, 41, 43, 44) mis en action par la poussée de moyens élastiques (16) et mis hors service en marche normale par une poussée inverse du fluide de servitude amené par des conduits (9, 34) dans un alésage aménagé dans la pièce intermédiaire (5) , poussée s 'exerçant de façon connue en soi sur un piston solidaire du poussoir (30, 1θ) contre lesdits moyens élastiques (16).1 - Improvement to the cylinder heads of reciprocating piston compressors with central aspiration wedged on the sleeve flange in elastic support against the cover of the cylinder head in a configuration known as "anti-liquid stroke" comprising a support by elastic setting of the valve (3) on the jacket (2) produced by means of an intermediate piece (5) whose contact surfaces on the cylinder head (51) and on the valve (3) form a sealed separation (35) of the high and low pressure chambers of the compressor, the sealing of the sliding of the intermediate piece (5) being ensured by at least two seals (6, 7) between which a circular groove (β) communicates with a conduit (34) arranged in the cylinder head (51) bringing a fluid pressurized service, characterized in that the support by elastic wedging of the valve (3) on the jacket (2) is produced by means of the intermediate piece (5) in which is arranged a pusher (30, 10) for controlling a device for load shedding (4, 41, 43, 44) put into action by the push of elastic means (16) and put out of service in normal operation by a reverse push of the service fluid supplied by conduits (9, 34) in a fitted bore in the intermediate piece (5), pushing exerted in a manner known per se on a piston secured to the pusher (30, 1θ) against said elastic means (16).
2 - Perfectionnement selon la revendication 1 caractérisé en ce que l'appui élastique de la pièce intermédiaire (5) contre le couvercle (19) réalisant le calage du clapet (3) sur la chemise (2) est assuré grâce à la pression du fluide de servitude permettant également le retrait du poussoir actionnant le dispositif de délestage (lθ) par l'intermédiaire d'une pièce de rupture (23, 15, 22, 18) en appui direct sur le couvercle (19).2 - Improvement according to claim 1 characterized in that the elastic support of the intermediate piece (5) against the cover (19) realizing the setting of the valve (3) on the jacket (2) is ensured by the pressure of the fluid service also allowing the removal of the pusher actuating the load shedding device (lθ) via a rupture part (23, 15, 22, 18) in direct support on the cover (19).
3 - Perfectionnement selon les revendications 1 ou 2 appliqué à un compresseur sec à double effet et caractérisé en ce que la chemise3 - Improvement according to claims 1 or 2 applied to a dry double-acting compressor and characterized in that the jacket
(65) est fermée par des clapets (3, 63) à aspiration centrale, calés par deux pièces d'appui (5, 69), l'ensemble étant empilé dans un même alésage de la culasse (61, 83) et mis en appui sur une entretoise-couvercle (62) recouvrant le carter-cylindresrenfermant les
pistons (81) du modèle de base lubrifié, auxquels sont connectés les pistons secs (66) par des tiges (78) coulissant de façon étanche à travers les pièces intermédiaires (69) et les clapets (63) inférieurs, la pièce intermédiaire inférieure (69) étant usinée de manière à recevoir un dispositif d'étanchéité (70) au passage de la tige (78) de liaison des pistons (66, 81 ) en lieu et place du système de commande du poussoir de délestage (30).(65) is closed by valves (3, 63) with central suction, wedged by two support pieces (5, 69), the assembly being stacked in the same bore of the cylinder head (61, 83) and put in support on a spacer-cover (62) covering the cylinder block enclosing the pistons (81) of the basic lubricated model, to which the dry pistons (66) are connected by rods (78) sliding in leaktight manner through the intermediate parts (69) and the lower valves (63), the lower intermediate part ( 69) being machined so as to receive a sealing device (70) at the passage of the rod (78) connecting the pistons (66, 81) in place of the control system of the load shedding pusher (30).
4 - Perfectionnement selon la revendication 3 caractérisé en ce que la pièce intermédiaire inférieure (69) est en appui étanche (75) sur une surface usinée de l'entretoise-couvercle (62).4 - Improvement according to claim 3 characterized in that the lower intermediate part (69) is in sealed support (75) on a machined surface of the spacer-cover (62).
5 - Perfectionnement selon la revendication 3 caractérisé en ce que la pièce intermédiaire inférieure (69) coulisse de façon étanche (88) dans un alésage du couvercle-entretoise (62) en cas de soulèvement accidentel du clapet inférieur (63) contre un moyen élastique (87) ; le compresseur sec est ainsi muni dans les deux sens d'un clapet "anticoup de liquide", la chemise (65) étant alors bloquée en translation dans son alésage de la culasse (61) par un goujon s'engageant dans une gorge (90).5 - Improvement according to claim 3 characterized in that the lower intermediate part (69) slides in sealed manner (88) in a bore of the spacer-cover (62) in the event of accidental lifting of the lower valve (63) against an elastic means (87); the dry compressor is thus provided in both directions with a "liquid shock" valve, the jacket (65) then being blocked in translation in its bore of the cylinder head (61) by a stud engaging in a groove (90 ).
6 - Perfectionnement selon la revendication 3 caractérisé en ce que le clapet inférieur (63) a ses deux plaques (92, 93) assemblées par une douille filetée centrale (64) dont l'alésage intérieur où coulisse la tige (78) de liaison des pistons est muni de joints d'étanchéité (37).6 - Improvement according to claim 3 characterized in that the lower valve (63) has its two plates (92, 93) assembled by a central threaded sleeve (64) whose inner bore where the rod (78) for connecting the pistons is fitted with seals (37).
7 - Perfectionnement selon l'une quelconque des revendications 3 à 6 caractérisé en ce que la culasse (61, 83) du compresseur sec est constituée de deux culasses (51) de compresseur du type à pistons lubrifiés, empilées et séparées par une entretoise (91) recevant les chemises (65), la culasse (51) inférieure reposant en position inversée sur la plaque entretoise-couvercle (62) du bloc de base. 8 - Perfectionnement aux culasses de compresseurs selon la revendication 1 appliquée à un compresseur à double effet construit sur une base de compresseur à simple effet caractérisé en ce que la culasse du compresseur double effet est constituée de deux culasses (51) du compresseur simple effet (1) empilées et séparées par une entretoise (91) recevant les chemises (65) des cylindres double effet, la culasse (51) inférieure reposant, en position inversée, sur une plaque entretoise-couvercle (62) du bloc de base.
7 - Improvement according to any one of claims 3 to 6 characterized in that the cylinder head (61, 83) of the dry compressor consists of two compressor cylinder heads (51) of the lubricated piston type, stacked and separated by a spacer ( 91) receiving the liners (65), the lower cylinder head (51) resting in the inverted position on the spacer-cover plate (62) of the base block. 8 - Improvement to the compressor heads according to claim 1 applied to a double-acting compressor built on a single-acting compressor base characterized in that the cylinder head of the double-acting compressor consists of two cylinder heads (51) of the single-acting compressor ( 1) stacked and separated by a spacer (91) receiving the liners (65) of the double-acting cylinders, the cylinder head (51) resting, in the inverted position, on a spacer-cover plate (62) of the base block.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR7737728A FR2411982A1 (en) | 1977-12-14 | 1977-12-14 | IMPROVEMENT OF PISTON COMPRESSOR CYLINDER HEADS, ESPECIALLY REFRIGERATING FLUID |
FR7737728 | 1977-12-14 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1979000386A1 true WO1979000386A1 (en) | 1979-06-28 |
Family
ID=9198855
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/FR1978/000034 WO1979000386A1 (en) | 1977-12-14 | 1978-10-17 | Improvements to cylinder heads of piston compressors,particularly for refrigerating fluids |
Country Status (7)
Country | Link |
---|---|
EP (1) | EP0010090A1 (en) |
BE (1) | BE872003A (en) |
ES (1) | ES475358A1 (en) |
FR (1) | FR2411982A1 (en) |
IT (1) | IT1108394B (en) |
PT (1) | PT68806A (en) |
WO (1) | WO1979000386A1 (en) |
Citations (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR358243A (en) * | 1904-10-06 | 1906-02-02 | Walter Henry Webb | Gas compressor |
GB270214A (en) * | 1926-01-23 | 1927-04-25 | Arthur Guy Enock | Improvements in valve mechanism for air or gas, pumps or compressors |
GB353582A (en) * | 1930-05-17 | 1931-07-30 | George Henry Turton Rayner | Improvements in valve apparatus for air compressors |
US1901478A (en) * | 1932-03-29 | 1933-03-14 | Gen Machinery Company | Compressor and valve therefor |
US2387117A (en) * | 1941-03-24 | 1945-10-16 | Frick Co | Refrigeration system |
FR1026043A (en) * | 1949-10-18 | 1953-04-22 | Grasso S Machf En N V | Piston compressor produced by welding |
US2957620A (en) * | 1957-08-19 | 1960-10-25 | Automatic Power Inc | Compressor head assembly |
FR1441382A (en) * | 1965-07-31 | 1966-06-03 | Burckhardt Ag Maschf | Suction and discharge coaxial valve device for compressors and high pressure pumps |
US3347264A (en) * | 1963-12-23 | 1967-10-17 | Stuart E Bunn | Suction and discharge valve |
FR1534313A (en) * | 1967-08-16 | 1968-07-26 | Compressor valve with flow adjustment device | |
FR1572663A (en) * | 1967-06-20 | 1969-06-27 | ||
US3814546A (en) * | 1972-05-24 | 1974-06-04 | Smith G & Co Inc | Seal assembly for air compressor valve |
FR2257029A1 (en) * | 1974-01-09 | 1975-08-01 | Quiri & Cie Usines | Piston type refrigerator compressor - has pressure regulating springs between cover and valve inside piston chamber |
-
1977
- 1977-12-14 FR FR7737728A patent/FR2411982A1/en active Granted
-
1978
- 1978-10-17 WO PCT/FR1978/000034 patent/WO1979000386A1/en unknown
- 1978-11-13 IT IT69587/78A patent/IT1108394B/en active
- 1978-11-14 BE BE191723A patent/BE872003A/en unknown
- 1978-11-20 PT PT68806A patent/PT68806A/en unknown
- 1978-11-24 ES ES475358A patent/ES475358A1/en not_active Expired
-
1979
- 1979-07-03 EP EP78900220A patent/EP0010090A1/en not_active Withdrawn
Patent Citations (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR358243A (en) * | 1904-10-06 | 1906-02-02 | Walter Henry Webb | Gas compressor |
GB270214A (en) * | 1926-01-23 | 1927-04-25 | Arthur Guy Enock | Improvements in valve mechanism for air or gas, pumps or compressors |
GB353582A (en) * | 1930-05-17 | 1931-07-30 | George Henry Turton Rayner | Improvements in valve apparatus for air compressors |
US1901478A (en) * | 1932-03-29 | 1933-03-14 | Gen Machinery Company | Compressor and valve therefor |
US2387117A (en) * | 1941-03-24 | 1945-10-16 | Frick Co | Refrigeration system |
FR1026043A (en) * | 1949-10-18 | 1953-04-22 | Grasso S Machf En N V | Piston compressor produced by welding |
US2957620A (en) * | 1957-08-19 | 1960-10-25 | Automatic Power Inc | Compressor head assembly |
US3347264A (en) * | 1963-12-23 | 1967-10-17 | Stuart E Bunn | Suction and discharge valve |
FR1441382A (en) * | 1965-07-31 | 1966-06-03 | Burckhardt Ag Maschf | Suction and discharge coaxial valve device for compressors and high pressure pumps |
FR1572663A (en) * | 1967-06-20 | 1969-06-27 | ||
FR1534313A (en) * | 1967-08-16 | 1968-07-26 | Compressor valve with flow adjustment device | |
US3814546A (en) * | 1972-05-24 | 1974-06-04 | Smith G & Co Inc | Seal assembly for air compressor valve |
FR2257029A1 (en) * | 1974-01-09 | 1975-08-01 | Quiri & Cie Usines | Piston type refrigerator compressor - has pressure regulating springs between cover and valve inside piston chamber |
Also Published As
Publication number | Publication date |
---|---|
BE872003A (en) | 1979-03-01 |
FR2411982B1 (en) | 1981-03-20 |
ES475358A1 (en) | 1979-04-01 |
IT7869587A0 (en) | 1978-11-13 |
FR2411982A1 (en) | 1979-07-13 |
PT68806A (en) | 1978-12-01 |
EP0010090A1 (en) | 1980-04-30 |
IT1108394B (en) | 1985-12-09 |
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