JPS62240484A - Gas compressor - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a gas pressure system, in detail, gas pressure using a piston that reciprocates in a cylinder. 'About the machine.

Gas compressors of the type described utilize one or many pistons that reciprocate within a cylinder.

Such gas compressors are used to fill the reservoirs of the pressure and air brake systems of heavily loaded vehicles with compressed air. The bearings of such press machines are usually lubricated by pressurized oil from the car's carton system, and the problem encountered here is the accumulation of oil that drains from the bearings into the press machine crankcase. Excessive slippage of the cylinder bore may occur due to
The result may be excessive drawing of oil into the shell of the system. Such oil entrainment may be harmful to the system and should desirably be eliminated or prevented. One obvious way to reduce such oil entrainment is to limit the flow of oil to the pressure machine bearings, but this may seriously impair the working life of the pressure km.

The object of the invention is to provide an improved pneumatic machine which makes it possible to substantially reduce the oil draw-in without undesirably reducing the oil flow to the bearings. .

In order to solve this problem, the present invention includes an assembly of a crankcase and a cylinder, and this assembly causes a piston to move back and forth within the cylinder to alternately achieve a suction stroke and a compression stroke. It has a rotatable crankshaft connected to a piston K114 by a crank bin,
In the air pressure range, where the crank 41II rotates in bearings that are lubricated by wall pressure from a source of lubricant, the crankcase generates a pressure rise in the crankcase and is no longer in the feedstock. A valve, which closes during the suction stroke, is provided to eliminate excess lubricant through the agent outlet passage.

According to one embodiment of the invention, the valve that closes during the suction stroke is arranged such that it closes during the suction stroke, while allowing free flow of air into the crankcase during the registration stroke. Alternatively, it may consist of a check valve. In general, the reverse valve can provide a restricted flow bypass to limit the pressure build-up that may be created in the crankcase.

In another preferred embodiment of the invention, the valve can consist of a passage that is hidden by a part of the crankshaft during part of the suction stroke.

Embodiments of the present invention will be explained below with reference to the drawings.

In FIG. 7, a single cylinder piston compressor, shown here in cross-section, has a valve plate and cylinder head J, and a crankcase casting l. The casting 1 has a cylinder bore, through which a piston S reciprocates by means of a crankshaft 4. This crankshaft 6 is connected to the piston by a connecting rod 7 and a gudgeon pin &. The crankshaft can rotate in respective bearings wo and 10, which are fed with pressure from the left-hand end of the crankcase, which is provided with a hydraulic chamber ll.

Pressure is supplied to this hydraulic chamber with oil from the engine,
To this engine, the pressure rear end is mounted with a suitable flange. The crankshaft y#/, 7 carries a drive pinion (not shown) which can be mated with a gear train in the engine crankcase.

The oil passage that reaches the connection between the oil chamber ll, the big end bearing and the left hand main bearing is indicated by the dashed lines lda and 1src,
During operation, leakage of oil flow should occur at the crank, shown as being closed by a suitable cover plate (as shown in Figure #1 (and as shown in dotted outline in the diagram)). 1 runs downward into the lower part. Here, a small upward oil passage Rf'L is provided.
This communicates at a low level to a reservoir in the lower part of the crankcase. Roughly speaking, tJ! is indicated by the symbol L at a relatively high point on the crankcase! , a somewhat larger air leaf intake passage is provided - shown in dotted lines in Figure 1.

The angular position of this air passage with respect to the rotation of the crankshaft is such that it is hidden by the approach of the outer surface -0 of the crank web counterweight 21 during the suction stroke of the crankshaft-piston assembly. Since only one selected passageway 19 is the breathing passageway for the crankcase, the inner end of the passageway 19 and the outer surface of the crank web 21 -2
0 constitutes a two-tense valve capable of interfering with crankcase breathing for a predetermined interval during rotation cycle C.

In FIG. 1, the direction of rotation of the crankshaft is indicated by an arrow here, and the crank web 21 is indicated by a dotted outline. As can be roughly seen, at the appropriate angular position moving away from the dead center of section m, after the completion of the compression stroke, the face O of the counterweight of the crank web hides the inner end of the passage l. I try to do that.

The effect of this is to immediately straddle the previously free flow of air into and out of the crankcase, whereby the downward movement of the piston is controlled by the oil above plate l. An appropriate pressure rise can be generated which acts in such a direction as to force the . By such means, the pre-leakage level in the crankcase of the compressor is effectively limited to a rail predetermined by the position of the passage IS.

The passage ttr and large passage 190 dimensions, along with the range of angular positions of the crankshaft that close passage 19 during the suction stroke, are selected to resist the tendency of oil to build up within the crankcase.

On the other hand, producing periodic pressure increases in the crankcase above a minimum value is not a risk, as this may reduce the efficiency of the compressor, which also has the opposite effect, reducing the lubricant This is undesirable, as it may cause it to pass through the piston rings and be forced upwardly into the compression chamber of the compressor.

%l' as described above and as illustrated in diagram #J
The method of achieving the same result as described above with reference to Figures 1 and 2 is to replace the passage 19 with a suitable check valve, 7.
In this case, the characteristics of the check valve should be carefully selected in order to avoid periodic high pressure increases in the crankcase during operation, which are undesirable for fX reasons as mentioned above. However, it is desirable to provide a possible bypass for this purpose.

In the cord compression machine described above with reference to Figures 11 and 11, whether or not this invention works correctly depends on whether or not the compressor is always installed in the position designed in connection with this invention. , depends on. To achieve positioning in a range of different but predetermined positions, the crankcase can be provided with a number of passages such as All other passageways will be blocked as necessary.

The purpose of this invention is to create an acceptable crankcase pressure to expel excess oil. In the case of a single cylinder compressor, this is achieved by closing the valve during the suction stroke, but with many cylinders in a common crankcase volume fji1, the crankcase volume such that there are intervals that result in a net reduction of
It may be necessary to arrange the relative periodic position of the piston to close the valve arrangement at this particular interval.

Kneading still necessarily occurs during the suction stroke of at least one such cylinder.

[Brief explanation of drawings]

F/Figure shows the piston cylinder type air pressure l based on this equation 9.
It is a partial sectional view of P paper. frIλ diagram is W1 diagram KIJ
! It is a slow gI11 side view. Figure 3 is a partial view of another embodiment. In the drawing, l is a crankcase and cylinder assembly, 5 is a piston, 6 is a crankshaft, 9 and IO are bearings, l
21 is a part of the crankshaft, and 23 is a reverse valve.

Claims (1)

[Claims] 1. An assembly (1) of a crankcase and a cylinder,
This assembly is connected to a rotatable crankshaft (6) connected to the piston by a crank pin for reciprocating the piston (5) within the cylinder to alternately achieve a suction stroke and a compression stroke. ) in which the crankshaft (6) rotates in bearings (9, 10) which are pressurized lubricated from a source of lubricant, the crankcase having a to generate a pressure rise,
Valves (19, 2) are closed during the suction stroke to eliminate excess lubricant from this through the lubricant outlet passage (18).
0). A gas compressor comprising: 2. A gas according to claim 1, wherein the valve comprises a check valve (23) that allows air to flow outwardly from the crankcase, but not inwardly into it. compressor. 3. The gas compressor according to claim 2, wherein the check valve includes a bypass passage for limiting pressure rise in the crankcase. 4. Gas compressor according to claim 1, wherein the valve is formed by a part (21) of the crankshaft of the compressor which hides the breathing passage (19) during the suction stroke. 5. The gas compressor according to claim 4, wherein the part (21) is a crank web counterweight part of the crankshaft (6).