MXPA97005019A - Girato compressor - Google Patents

Abstract

In a vertical, double-cylinder, hermetic, piston-wound, vertical lift compressor, a high-pressure gas portion is divided from the chamber defined by the lower muffle and pump support to the axial bore of the crankshaft. The crankshaft extends to the oil well in such a way that the rotation of the arrow produces a pumping action to pump the oil from the well to the structure that requires lubrication. Additionally, the flow is divided from the chamber to the axial orifice that produces a jet pump effect which supplements the pumping action produced by the rotation of the arrow, particularly in the speed ba

Description

ROTATING COMPRESSOR BACKGROUND OF THE INVENTION In vertical hermetic compressors it is a common practice to use the rotary shaft as a centrifugal pump to pump the lubricant from the well to locations requiring lubrication. Gradually, centrifugal pumps have speed dependent. With the wider use of variable speed motors, it is possible to operate a compressor in a speed range that provides inadequate lubrication. Because the gas is discharged from the compression chamber against the deflection of the discharge valve in combination with the fluid pressure in the muffler acting on the downstream portion of the discharge valve, the pressure of the gas passing to the through the valve inlet in the muffler can be of an order of 0.3515 kg / cm2 (5 psi) greater than anywhere in the compressor. In the case of a double cylinder, hermetic fixed-blade compressor or vertical roller piston, one of the mufflers is secured to the marked side of the pump and extends to the oil well. According to this, the highest gas pressure is available in the oil well. The present invention uses this higher gas pressure to assist in the pumping of lubricant. Specifically, a portion of the gas, which discharges from the lower part of the cylinder and which bears retained oil, is directed to the hole in the arrow which serves as a centrifugal pump. The gas passes into the hole that acts as a jet pump in relation to the oil in the well, thereby supplying the pumping action of the centrifugal pump to supply lubricant to the structure that requires lubrication. It is an object of this invention to improve lubrication in low speed operation. It is another object of this invention to assist in the pumping of lubricant when a higher lifting height is required due to the low level of the well. These objects, and others as they will become apparent in the following, are realized by the present invention. Basically, a portion of compressed gas is discharged from the bottom of a vertical single cylinder compressor or a lower cylinder of a vertical double cylinder compressor is directed into the hole of the shaft which acts as a centrifugal pump. The portion of the gas directed in the orifice coactuates with the oil well in the nature of a jet pump by which it aids the centrifugal pump in pumping oil. BRIEF DESCRIPTION OF THE DRAWINGS For a better understanding of the present invention, the reference should be made with the following detailed description thereof taken together with the accompanying drawings in which: Figure 1 is a partially divided, partial view of a vertical compressor employing the present invention; and Figure 2 is a partial, partially divided view, taken approximately 90 ° from the view of Figure 1. In Figures 1 and 2, the number 10 generally designates a hermetic, double cylinder, lift-up piston compressor. lateral, vertical that has a cover 12. There are two pump assemblies which, together, build a cartridge pump. The primary assembly or lower pump includes the cylinder 20 which has an interior part 20-1. The annular piston 22 is located on the inside of the cylinder 20-1 and receives the eccentric stump 16-1 of the eccentric shaft 16 in the inner hole 22-1. The vane 24 is located in a vane opening (not shown) and deviates in the contact rail with the piston 22 by the spring 25 and divides the space-increasingly between the piston 22 and the hole 20-1 in one direction. suction chamber and a discharge chamber. The pump support 26 is below the hole 20-1 and the piston 22 while receiving the stump defining the lower end 16-3 of the arrow 16 in a support relationship. The pump support 26 is secured at a location in the cylinder 20 by a plurality of circumferentially spaced screws. 2. 3 . The discharge valve 27 and the stop valve 28 are secured to the support 26 in such a way that the discharge valve 27 co-acts with the valve retainer 28 and the discharge inlet 26-1 on the support 26 of the pump. The muffler 30 is secured to the support 26 by screws 32 and coact with them to define the chamber 31. It should be noted that only the difference between the screws 29 and 32 is that the screws 32 additionally secure the muffle 30 to the support 26. The assembly Secondary or upper pump is similar to the first lower assembly or pump described above and includes the cylinder 40 which has a lower part 40-1. The annular piston 42 is located in the hole 40-1 of the cylinder and receives the eccentric stump 16-2 of the eccentric arrow 16 in the hole 42-1. The vane 44 is located in a vane opening (not shown) and deflected in a contact path with the piston 42 by the spring 45., and, divides the space increasingly between the piston 42 and the lower part 40-1 in a suction chamber and a discharge chamber. The motor support 46 is located in the upper part of the hole 40-1 and the piston 42 while receiving the stump defining the upper portion 16-4 of the arrow 16 in a support relationship. The motor support 46 is secured at a location on the cylinder 40 by a plurality of circumferentially spaced screws, 49 which corresponds to the screws 29. The discharge valve 47 and the valve retainer 48 are secured to the support 46 in such a way that the discharge valve 47 coact with the valve retainer 48 and the discharge inlet 46-1 in the motor support 46. The muffle 50 is secured to the support 46 by the screws 52 and co-acts with them to define the chamber 51 which communicates with the interior of the cover 12 by means of the inlets 50-1. It should be noted that only the difference between the screws 49 and 52 is that the screws 52 additionally secure the muffle 50 to the support 46. The cylinders 20 and 40 are provided with openings 20-2 and 40-2, respectively, which receive the plate. 60 separator in them. The plate 60 and the support 26 provided with seal, contacted together by lubricant, respectively, with the upper part and the lower part of the piston 22 and the vane 24 while the plate 60 and the motor support 46 are provided with seal, contacted by lubricant with the lower and upper part, respectively, of the piston 42 and the vane 44. Additionally, the plate 60 coact with the openings to locate radially between the cylinders 20 and 40 with respect to each other, and align coaxially the trunnion supports 16-3 and 16-4 of arrow 16 with supports 26 and 46.

In operation, the compressor 10 is driven by an electric motor that includes the stator 18, which is secured to the cover 12, and the rotor 19 which is secured to the arrow 16 and which rotates as a unit with it. The rotation of the arrow 16 produces a centrifugal pumping effect which sucks the oil from the well 36 into the hole 16-5 and supplies it to the feed passages 16-6 to 16-9 to lubricate the various members, as is conventional . The coercion of the vanes 24 and 44 with the pistons 22 and 42, respectively, creates a reduced pressure that tends to suck the gas from the air conditioning or cooling system (not shown). The gas passes in series through the suction line 13 and the tube 14 to the radial bottom 20-3 which is directed directly into the hole 20-1. As best shown in Figure 1, the radial bore 20-3 is also connected to the axial and series bore 20-4 by means of the axial bores 60-1 and 40-3 with the bore 40-1. The compressed gas in the cylinder 20, as best shown in Figure 2, passes through the inlet 26-1 into the chamber 31. The gas in the chamber 31 can pass through both the trajectories towards the chamber 51. as indicated in the axial holes 20-5 and 20-6 in the cylinder 20 and the axial holes 40-4 and 40-5 in the cylinder 40. In the path illustrated in Figure 2, the compressed gas in the chamber 31 it passes in series through the holes 26-2 and 20-5, 60-2, 40-4 and 46-2 towards the chamber 51. The compressed gas in the cylinder 40 passes through the inlet 46-1 towards the chamber 51. The gas from chamber 51 passes through inlets 50-1 inside cover 12 and releases the discharge (not shown). Additionally, according to the teachings of the present invention a third flow path is provided from the chamber 31 in the muffle 30. The tube 34 is sealed connected to the muffle 30 and provides a fluid path from the chamber 31 to the orifice 16. -5 on the arrow 16. During discharge, the gas pressure in the mufflers 30 and 50 is slightly higher, approximately 0.3515 kg / cm2 (5 psi), more than the pressure in the cover 12 and this causes the discharge drives . The discharge drives in the muffler 30 cause a portion of the gas in the muffle 30 to flow through the tube 34 in the hole 16-5 in the arrow 16 whereby a substantial energy is supplied which aids in the delivery of oil from the muffler. Well 36 through hole 16-5 to feed the passages. 16-6 to 16-9. Passing the elevated gas pressure from tube 34 to port 16-5 produces a jet pump effect with respect to well oil 36. The actual contribution of flow through tube 34 is a function of engine speed, the level of the oil well, the magnitude of pressure fluctuations, and the specific pumping mechanism if it is centrifugal, as illustrated, or positive displacement. However, the jet pump effect provides a pumping aid when this is most needed, in low speed operation. Although a preferred embodiment of the present invention has been illustrated and described, other changes may be made by those skilled in the art. For example, the present invention is applicable to a piston compressor wound in vertical form of single cylinder side elevation. The greatest requirement is the presence of a muffler in the lower part 30, or its equivalent, and it is common to use two mufflers in a single cylinder compressor for additional sound reduction. Also a simple muffler can be used on the bottom of the cylinder, if necessary or desired. Additionally, a positive displacement pump can be used more than a centrifugal pump and still obtain the benefits of the present invention. Therefore, it is intended that the scope of the present invention be limited only by the scope of the appended claims.

Claims (6)

1. CLAIMS 1. A hermetic rotary compressor means, vertical side elevation, characterized in that it comprises: a cover means; a pump mounting means located on the cover; a motor means located in the cover means above the pump mounting means; an arrow means rotatably driven by the motor means and extending downwardly through the pump mounting means into the oil well located in the lower part of the cover means; the arrow means coact with the pump mounting means to cause the pump mounting means to compress the gas and which includes the oil distribution means extending from the oil well; the support means secured to the pump mounting means and supporting the received arrow means; the muffle means secured to the support means and coacting therewith to define a chamber in fluid communication with the pump assembly via the discharge valve means whereby the compressed gas in the pump assembly is supplied to the chamber;
2. a first fluid path for directing most of the compressed gas supplied to the muffler means in the cover means; a second fluid path for directing a small amount of compressed gas supplied to the muffler means in the oil distribution means whereby the compressed gas passes into the oil distribution medium which co-acts with the oil in the well to produce an oil. effect of jet pump that helps in the supply of oil from the well to the oil distribution medium. The compressor means according to claim 1, characterized in that the oil distribution means includes an axially extending orifice in general communicating the arrows with at least the communication of the radially extending orifice with the extending orifice. axially in general.
3. 3. The compressor means according to claim 1, characterized in that the second fluid path extends through a portion of the oil well.
4. The compressor means according to claim 1, characterized in that the pump mounting means includes a lower-and upper pump assembly.
5. 5. The compressor means according to claim 4, characterized in that the muffler means is secured to the lower pump assembly.
6. 6. The compressor means according to claim 5, characterized in that it also includes the muffler means secured to the upper pump assembly and forming a part of the first fluid path.