Gas/oil mist generator
阅读说明:本技术 气/油雾发生器 (Gas/oil mist generator ) 是由 D·瓦尔特 于 2020-04-17 设计创作,主要内容包括:一种气/油雾发生器(1、1A),包括:蓄积腔室(2),在蓄积腔室(2)内积聚空气中的油粒雾,该蓄积腔室(2)设有至少一个第一雾出口(4),至少一个雾化器(3、3A)供给到所述蓄积腔室(2)中,其中所述蓄积腔室(2)与压差调节器(12)相关联,当所述蓄积腔室(2)的内部压力和雾化器供应压力(3)之间的差超过预定阈值时,所述压差调节器将压缩空气供给到蓄积腔室中。(An air/oil mist generator (1, 1A) comprising: -an accumulation chamber (2) inside which the mist of oil particles in the air accumulates, the accumulation chamber (2) being provided with at least one first mist outlet (4), into which accumulation chamber (2) at least one atomizer (3, 3A) is fed, wherein the accumulation chamber (2) is associated with a differential pressure regulator (12) which feeds compressed air into the accumulation chamber when the difference between the internal pressure of the accumulation chamber (2) and the atomizer supply pressure (3) exceeds a predetermined threshold value.)
1. An air/oil mist generator (1, 1A) comprising: an accumulation chamber (2) within which the mist of oil particles in the air accumulates, the accumulation chamber (2) being provided with at least one first mist outlet (4); and at least one nebulizer (3, 3A) that opens into the accumulation chamber (2), wherein the accumulation chamber (2) is associated with a differential pressure regulator (12), the differential pressure regulator (12) supplying compressed air into the accumulation chamber when the difference between the internal pressure of the accumulation chamber (2) and the nebulizer supply pressure (3) exceeds a predefined threshold value.
2. The generator according to claim 1, wherein the differential pressure regulator (12) comprises a valve element (13), the valve element (13) being loaded by a spring (14) in the direction of an opening (15) communicating with a source of pressurized air, the spring (14) and a portion of the valve element (13) communicating with the accumulation chamber (2) so that, when the pressure in the accumulation chamber (2) drops below a threshold defined by the load of the spring on the valve element (13), the valve element (13) releases the opening (15) to allow air to flow from the source of pressurized air to the accumulation chamber (2).
3. The generator according to claim 1, wherein the outlet of the differential pressure regulator (12) inside the accumulation chamber (2) comprises a muffler (16).
4. A generator (1, 1A) according to claim 1, wherein the atomizer (3, 3A) comprises a first nozzle (7, 7A) supplied with pressurized air, having at least a first channel (8, 80) supplied with pressurized air, each channel (8, 80) being provided with an outlet (8A, 8A') on a surface (70) of the first nozzle, which surface (70) at least partially defines a first chamber (9) axisymmetric with respect to the axis (A), the channels (8, 80) being oriented so as to generate a rotation around said axis (A) of the air introduced into the first chamber (9), the surface (70) of the first nozzle providing at least one convergent portion towards the outlet orifice (10, 10A), the atomizer (3, 3A) further providing a second nozzle (6) supplied with oil, so that the oil is sucked through the second nozzle (6) by the air flow through the first chamber (9).
5. A generator according to claim 4, wherein the outlet orifice (10) of the first nozzle (7) flows into a diverging channel (11).
6. The generator according to claim 5, wherein the divergent passage (11) is defined by a wall (120), the wall (120) being spaced (M2, M1) with respect to the periphery of the outlet orifice (11), at least in a plane containing the outlet portion of the orifice.
7. The generator according to claim 3, wherein the outlet aperture (10) faces a condenser (5) arranged inside the accumulation chamber (2).
8. A generator according to claim 3, wherein the outlet of the second nozzle (6) faces the outlet (8A, 8A ') of the channel (8, 80), preferably midway of the outlet (8A, 8A').
9. The generator according to claim 3, wherein the second nozzle (6) has a supply channel that sucks oil present in liquid form inside the accumulation chamber (2), the supply channel comprising a flow regulator (52).
10. Generator according to one or more of the preceding claims, wherein the nebuliser (3) is fed by a first line (BA) of compressed air at a first pressure, and there is a further nebuliser (3A) also open into the accumulation chamber (2) fed by a second line (AL) of compressed air at a second pressure higher than the first pressure, optionally associated with a non-return valve (807), which non-return valve (807) prevents a counter-flow from the accumulation chamber (2).
11. Lubrication system comprising a generator (1, 1A) according to one or more of the preceding claims.
Technical Field
The invention relates to an air/oil mist generator. In particular, the present invention relates to a mist generator for use in a lubrication system.
Background
In the field of lubrication, mist generators applying the venturi principle are known. One of these systems is currently marketed by the applicant under the trade name NEBOL.
It comprises a venturi for injecting pressurized air axially thereto. In the throat portion (minimum passage portion) of the venturi, there is a nozzle conceived for sucking oil. In practice, the oil is drawn through the nozzle by the vacuum created by the venturi effect at the smallest passage section.
Alternative mist generating systems are also well known, such as those in which mixing is carried out without using a venturi system, but by means of a so-called vortex system, such as the one described in patent US 4,335,804.
The advantage of vortex systems over venturi systems is that they are more flexible. Indeed, the vortex is effective over a wider range of air pressures and flow rates (and is therefore self-supporting and produces a fog).
In practice, the pressure at which the system is used to generate the mist is derived from the difference between the supply pressure to the atomizer (whether venturi or vortex type) and the pressure in the mist storage chamber.
For example, if the supply pressure (of the passage) is 6 bar and the pressure of the chamber is 4 bar, the mist generation system will operate at a pressure of 2 bar.
The vortex system allows operation over a greater range of pressures and flow rates than the venturi system.
In all cases, the atomizer that generates the mist (whether venturi or vortex type) is fed to an accumulation chamber that is connected by an outlet to one or more user devices.
One problem encountered with known systems is the fact that: these systems are calibrated to operate in a pressure range close to normal line pressure (i.e., 6 bar). In fact, when the user equipment requires a certain air flow, the pressure difference created in the section across the nebulizer will create a vacuum in the accumulation chamber due to the required flow rate, thereby enabling the nebulizer to work.
When the user equipment requires an extremely high air flow rate, the pressure in the accumulation chamber will drop compared to the optimum amount of air/oil mist flow required, and the atomizer will generate too much mist, resulting in a waste of oil.
Disclosure of Invention
It is an object of the present invention to provide an air/oil mist generator which is improved over the known art.
Another object of the present invention is to provide a generator capable of preventing the waste of oil when an extremely high air flow rate is required.
Drawings
Further characteristics and advantages of the invention will become apparent in the description of a preferred but not exclusive embodiment of the device, illustrated by way of non-limiting example in the accompanying drawings, wherein:
FIG. 1 is a cross-sectional view of an atomizer as part of a generator according to the present invention;
FIG. 2 is a simplified cross-sectional view taken along line II-II of FIG. 1;
FIG. 3 is a simplified cross-sectional view of a detail of the generator;
FIG. 4 is an exploded view of the detail circled in FIG. 3;
FIG. 5 is an overall perspective view of a generator according to the present invention;
FIG. 6 is a schematic diagram of a lubrication system including the generator of FIG. 5;
FIG. 7 is a cross-sectional view of a variation of the generator according to the invention, having in particular two atomizers, a high-pressure atomizer and a low-pressure atomizer;
FIG. 8 is a plan view of a detail of the high pressure atomizer of FIG. 7;
FIG. 9 is a perspective view of the generator of FIG. 7; and
fig. 10 is a schematic diagram of a supply system for the generator of fig. 7 and 9.
Detailed Description
With reference to the above figures,
Reference must first be made to fig. 5, which shows a possible configuration of the generator. It may comprise a
It is conceivable to install a gauge 37 (fig. 6) on the outside of the
A door 36 equipped with a valve (e.g., a manual valve) may also be used to completely evacuate the
The
According to the invention, the generator comprises at least one
In the case shown, the
In the wording herein, the term "medium/low pressure" means that it is configured to work in an optimal way with an intake pressure of 4 to 8 bar, preferably between 5 and 6 bar.
It can be seen that the
The
The
In particular, the
The
The
As shown in fig. 1, the surface 70 of the first nozzle has at least one portion that converges towards the outlet orifice 10 (of said nozzle).
Advantageously, the area of the
Advantageously, the ratio between the total area of the
In the illustrated construction, the nozzle may be made in one piece and have a
Downstream of the
Returning to fig. 1, the known
It has been found that this distance M1 can improve the size of the particles fed into the
The distance M1 significantly affects the mass and size of the particles and it has been found that the minimum distance is at least half the diameter D1 of the outlet, preferably the minimum distance M1 is at least equal to the diameter D1 of the outlet.
The best measurement of M1 is comprised substantially between one and a half times the outlet diameter and 4.5 times the outlet diameter.
The diverging
Another feature that affects the oil particle size is the roughness of the
In fact, it is speculated that when a "peak" on the surface is encountered, the particle breaks further and becomes smaller. At the same time, a part of the larger particles are stopped in the surface grooves and are thus excluded from the flow.
The optimum roughness value of the walls of the diverging
Preferably, the roughness is obtained by a treatment that produces a helix on the surface, which ideally rotates counter to the direction of rotation of the vortex of air and oil.
The
Obviously, between the intermediate element and the
Advantageously, the
For the inflow of oil, the
For example, the
Advantageously, as shown in fig. 1, the
It has been found that for optimum atomiser performance it is preferred that the
Furthermore, the second nozzle is useful for axial output with respect to the
According to one aspect of the invention, the
The condenser may have dimensions such as to ensure that the indentations I obtained by the extension of the
It should be mentioned that, in the wording herein, the term "condenser" 5 is used to define a plate-
Even if the
It acts at best as a sort of shield that promotes coalescence of the larger-sized oil particles that strike the
Other possible configurations of the
The operation of the present invention will become apparent from the above description and is substantially as follows.
The
When the user equipment needs lubrication, the regulator R sends pressurized air to the nozzle 7 (e.g. via the groove 40 and the source 41).
The pressurized air flows through the
Inside the
Further, due to the relationship between the total area of the
Once the air mixed with oil exits through the
Only the lighter particles remain suspended in the air flowing through the diverging section and these fine particles diffuse within the
Assuming that the
The above structure generates within the accumulation chamber 2 a very fine mist of suspended oil particles of diameter less than about 1 μm, which mist is conveyed by the air flowing through the outlet 4.
The position of the outlet 4 on top of the chamber subjects the oil particles to a further choice, only very small and light particles being able to be transported by the compressed air coming out of the outlet 4.
The above system seeks to produce extremely small oil particles which form a very fine mist and which can be conveyed by the compressed air delivered by the
Obviously, particles that condense on the diverging
Advantageously, the
This can occur if the demand for lubrication air from the user equipment is particularly high and exceeds the demand that the atomizer can handle directly.
In this case, the differential pressure regulator 12 (fig. 3 and 4) carries the excess pressurized air inside the
In the depicted example, the
In order to prevent air from entering the chamber and negatively affecting the mist present therein, the outlet of the
In the above description, a
Systems such as those described above are suitable for use as machines (e.g. cutting)Machine) provides a medium range tool and therefore also requires a medium lubrication air flow rate, i.e. at 2-8m3Flow rate in the range of/hour.
In operations where lubrication and cooling are performed using tools requiring lower mist flow rates, the above system has been found to be scarcely applicable. More specifically, it has been found that at low flow rates, i.e. below 2m3The ability to produce a fine particle mist is significantly reduced at a flow rate per hour. This is because the back pressure present in the
As shown in fig. 7 to 10, the
In the drawings, the same reference numerals are used as those used for denoting components having functions similar to those already described.
It will be noted in particular from an analysis of fig. 7 that this generator is substantially similar to the one previously described and also has an
For example, the size of the
However, in this particular configuration, the atomizer has a
As previously mentioned, the characteristics of the
The simplification introduced by adding both the
It is clear that also in the case shown in fig. 1, i.e. in the case of a
Returning now to the description of the
For example, the
The essential difference with the
The
In practice, the two
This is evident from an analysis of fig. 8, which fig. 8 shows the configuration of the
This has a single passage 80 (or in any case a smaller number of
The remaining dimensions of the
In particular, again according to fig. 7, it is known that the
The height H1 of the diverging
The height H1 and/or H2 is preferably 1.5 times the outlet diameter D1, D2. Preferably, the heights H1, H2 are substantially twice the outlet diameter D1 and/or four times the outlet diameter D2.
The above values are particularly important; in practice, these specific measurements and angles are obtained by rather long and complex optimization procedures based on trial and error. The above ranges and sizes are those that optimize the performance of the device.
The air supply to the
The booster may be supplied to a suitable
The
To complete the description of the schematic in fig. 10, it is noted that the supply line BA of the
The
A predetermined amount of oil is supplied in advance, which is deposited at the bottom of the
Then, the line pressure (e.g. 6 bar) is provided to the
If no air is required by the other user device U1 or U2, the pressure within the
When the user equipment requires air, the pressure within the
For a standard air flow rate (e.g. when handling a standard sized tool) the internal pressure of the tank is reduced to the same level as the line pressure (i.e. about 5-6 bar).
In this case, both the
In fact, said
If the user equipment requires additional air flow rate, the pressure in the chamber may drop below the preset value. This is due to the fact that: the required air flow rate exceeds the maximum air flow rate that can be delivered by the
Under these conditions, the
Thus, under these conditions, the intervention of the differential pressure regulator 12 (also present in this configuration) eliminates the additional passage for feeding air directly into the
At the same time, if the required air flow rate is below the standard, and this happens for example when very small tools are used, the pressure in the
When the pressure exceeds a certain threshold (for example 6.5), the non-return valve 807 (for example set to a pressure difference of 0.5 bar) intervenes, completely shutting off the
When the
The gradual reduction of the flow rate of the
Thus, the system shown will automatically adapt to the required air flow rate and also maintain an optimum amount of mist for lubrication at low flow rates.
It should be noted that the increase in the lubrication pressure not only contributes to the generation of a very fine mist, but also makes it possible to cool more effectively small tools which receive more air and more oil, thus facilitating the cutting process described above. Higher air pressure also improves the removal of the shavings produced by the process.
According to a variant of the
This is useful because the production cost of the high-pressure air supplied to the
Thus, for example, the
Obviously, in a simplified embodiment, it is possible to simply envisage a valve (manual or automatic, controlled by the control unit) which activates the
Various embodiments of the invention are described herein, but other embodiments can be conceived using the same innovative concepts.
For example, the
Furthermore, it is possible to envisage, for example, an oil tank separate from (and suitably pressurized)
The construction of the
Furthermore, the
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