U.S. patent application number 14/358353 was filed with the patent office on 2015-08-06 for sealing glove for a cylinder of a compressor, compressor and cooling appliance.
This patent application is currently assigned to WHIRLPOOL S.A.. The applicant listed for this patent is WHIRLPOOL S.A.. Invention is credited to Dietmar Erich Bernhard Lilie, Henrique Bruggmann Muhle.
Application Number | 20150219095 14/358353 |
Document ID | / |
Family ID | 47471418 |
Filed Date | 2015-08-06 |
United States Patent
Application |
20150219095 |
Kind Code |
A1 |
Muhle; Henrique Bruggmann ;
et al. |
August 6, 2015 |
SEALING GLOVE FOR A CYLINDER OF A COMPRESSOR, COMPRESSOR AND
COOLING APPLIANCE
Abstract
A flexible sealing glove (100) applicable under radial tension
to aerostatic linear compressors (200), capable of sealing the
bearing channels (1, 2), which are located on the outer face (5) of
the cylinder (14). The flexible sealing glove (100) is made of
substantially polymeric material and its main functions are to
increase the efficiency and the yield of the compressor (200).
Inventors: |
Muhle; Henrique Bruggmann;
(Joinville SCbr, BR) ; Lilie; Dietmar Erich Bernhard;
(Joinville SC, BR) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
WHIRLPOOL S.A. |
Sao Paulo - SP |
|
BR |
|
|
Assignee: |
WHIRLPOOL S.A.
Sao Paulo, SP
BR
|
Family ID: |
47471418 |
Appl. No.: |
14/358353 |
Filed: |
November 14, 2012 |
PCT Filed: |
November 14, 2012 |
PCT NO: |
PCT/BR12/00452 |
371 Date: |
May 15, 2014 |
Current U.S.
Class: |
92/169.1 |
Current CPC
Class: |
F04B 39/121 20130101;
F04B 35/045 20130101; F04B 53/008 20130101; F16C 32/0622 20130101;
F04B 53/143 20130101; F04B 39/0292 20130101; F04B 39/06 20130101;
F16C 37/002 20130101; F16C 29/025 20130101; F04B 39/126
20130101 |
International
Class: |
F04B 53/14 20060101
F04B053/14; F04B 39/12 20060101 F04B039/12; F04B 39/06 20060101
F04B039/06 |
Foreign Application Data
Date |
Code |
Application Number |
Nov 16, 2011 |
BR |
PI1105470-0 |
Claims
1.-19. (canceled)
20. A sealing glove (100) for a cylinder (14) of an aerostatic
linear compressor bearing (200), the cylinder (14) being defined by
an outer surface (5) and an inner surface (4), the inner surface
(4) defining a through cavity inside the cylinder (14), capable of
enabling the linear movement of a piston (15) on its inside,
wherein the inner surface (4) of the cylinder (14) comprises a
plurality of distribution orifices (3) that communicate with the
outer surface (5), the outer surface (5) comprising bearing
channels (1,2) capable of communicating with said distribution
orifices (3), wherein the glove (100) is flexible and disposed on
the outer surface (5) of the cylinder (14) under radial tension,
the association between the outer surface (5) and the sealing glove
(100) defining bearing formation ducts (1',2') capable of directing
the bearing fluid to the distribution orifices (3), the sealing
glove (100) sealing the bearing channels (1,2) by means of
pressurizing the outer surface of the sealing glove (100).
21. The sealing glove (100) as claimed in claim 20, wherein the
bearing fluid flows over its inner surface through the bearing
channels (1',2') and acts on the interface (17) defined between the
outer surface of the glove (100) and the outer block (13)
constantly pressurizing the outer surface and the inner surface of
the sealing glove (100).
22. The sealing glove (100) as claimed in claim 21, wherein the
pressure of the bearing fluid that acts on the outer surface of the
sealing glove (100) is substantially equal to the discharge
pressure of the compressor (200).
23. The sealing glove (100) as claimed in claim 22, wherein the
pressure exerted on the outer surface of the sealing glove (100)
comprises a value equal to or greater than that of the pressure
that acts on the inner surface of the sealing glove (100).
24. The sealing glove (100) as claimed in claim 22, wherein the
bearing fluid is the cooling fluid.
25. The sealing glove (100) as claimed in claim 24, wherein the
sealing glove (100) is made substantially of polymeric
material.
26. The sealing glove (100) as claimed in claim 25, wherein the
sealing glove (100) is endowed with elastomeric properties.
27. The sealing glove (100) as claimed in claim 20, wherein the
sealing glove (100) comprises thermo-contractile material.
28. An aerostatic bearing linear compressor (200) comprising a
cylinder (14) defined by an outer surface (5) and an inner surface
(4), the inner surface (4) defining a through cavity inside the
cylinder (14) capable of enabling the linear movement of a piston
(15) on its inside, and the inner surface (4) of the cylinder (14)
comprises a plurality of distribution orifices (3) which
communicate with the outer surface (5), the outer surface (5)
comprising bearing channels (1,2) that communicate with said
distribution orifices (3), the linear compressor (200) comprising a
sealing glove (100) disposed on the outer surface (5) of the
cylinder (14) under radial tension, the association between the
outer surface (5) and the sealing glove (100) defining bearing
formation ducts (1',2') capable of directing the bearing fluid to
the distribution orifices (3), the outer surface of the sealing
glove (100) being pressurized.
29. The compressor (200) as claimed in claim 27, wherein the
bearing fluid flows over the inner surface of the sealing glove
(100) through the bearing channels (1',2') and acts on the
interface (17) defined between the outer surface of the glove (100)
and the outer block (13), constantly pressurizing the outer surface
and the inner surface of the sealing glove (100).
30. The compressor (200) as claimed in claim 29, wherein the
pressure of the bearing fluid that acts on the outer surface of the
sealing glove (100) is substantially equal to the discharge
pressure of the compressor (200).
31. The compressor (200) as claimed in claim 30, wherein the
pressure exerted on the outer surface of the sealing glove (100)
comprises a value equal to or greater than that of the pressure
which acts on the inner surface of the sealing glove (100).
32. The compressor (200) as claimed in claim 31, wherein the
bearing fluid is the cooling fluid.
33. The compressor (200) as claimed in claim 32, wherein the
sealing glove (100) is made of polymeric material.
34. The compressor (200) as claimed in claim 33, wherein the
sealing glove (100) is endowed with elastomeric properties.
35. The compressor (200) as claimed in claim 34, wherein the
bearing formation ducts (1',2') comprise feeder channels (2) and
restriction channels (1).
36. The compressor (200) as claimed in claim 35, wherein the
restriction channels (1) are disposed radially in relation to the
axial center Cr) of the compressor (200).
37. The compressor (200) as claimed in claim 36, wherein the feeder
channels (2) are disposed in parallel to the axial center (`X`) of
the compressor (200).
38. A cooling appliance comprising a cylinder (14) of an aerostatic
linear compressor bearing (200), the cylinder (14) being defined by
an outer surface (5) and an inner surface (4), the inner surface
(4) defining a through cavity inside the cylinder (14), capable of
enabling the linear movement of a piston (15) on its inside,
wherein the inner surface (4) of the cylinder (14) comprises a
plurality of distribution orifices (3) that communicate with the
outer surface (5), the outer surface (5) comprising bearing
channels (1,2) capable of communicating with said distribution
orifices (3), said cooling appliance further comprising a sealing
glove (100), wherein the sealing glove (100) is flexible and
disposed on the outer surface (5) of the cylinder (14) under radial
tension, the association between the outer surface (5) and the
sealing glove (100) defining bearing formation ducts (1',2')
capable of directing the bearing fluid to the distribution orifices
(3), the sealing glove (100) sealing the bearing channels (1,2) by
means of pressurizing the outer surface of the sealing glove (100).
Description
[0001] The present invention refers to a flexible glove for sealing
bearing fluid channels of an aerostatic bearing compressor, more
particularly aerostatic bearing compressors applied to cooling
systems.
DESCRIPTION OF THE STATE OF THE ART
[0002] As a general rule, a cooling cycle comprises four essential
elements, namely a compressor, a condenser, an expansion valve and
an evaporator. In this cooling cycle, a cooling fluid (Freon.RTM.,
for example) circulates through said components where the following
operations occur. In the expansion valve, the cooling fluid which
is found originally in liquid form, expands to enter into a gaseous
and rarefied form, decreasing its own temperature. Subsequently,
this fluid, now with lower density, passes through an evaporator
enabling it to absorb heat from the environment. Next, the fluid
comes to a compressor which compresses the fluid returning it to
liquid form (or compressed gaseous form). Lastly, the fluid passes
through a condenser transmitting heat to a second environment, and
these stages restart when the fluid returns to the expansion valve,
thus concluding the cooling cycle.
[0003] Cooling compressors may present various different forms,
mechanisms and functions. Each type of compressor is better adapted
to a certain type of application, and a compressor model widely
known in the state of the art is the linear compressor. This
compressor operates by way of the axial and oscillatory movement of
a piston inside a cylinder.
[0004] The gas that enters into a linear compressor proceeds along
the following path: firstly the gas penetrates into a plenum
chamber, next it passes through an inlet valve and soon after fills
a region called the compression chamber, that is, a region
comprised by the space between the piston and the cylinder of the
compressor where there occurs compression capable of transforming
it into a liquid or gas having greater density. In a third moment,
this fluid, now having greater density, is displaced through a
discharge valve and lastly, the fluid fills a region called the
discharge chamber from where it is released for the next stages of
the cooling cycle.
[0005] It is noted that for correct working, linear compressors
need lubrication between the outer face of the piston and the inner
face of the cylinder. The purpose of said lubrication is to
decrease attrition between the parts, whereby increasing the yield
of the compressor and avoiding premature wear and tear of its
parts. Accordingly, there are linear bearing compressors with
viscous fluids, of the lubricant oil type and linear bearing
compressors with gaseous fluids.
[0006] Linear bearing compressors with gaseous fluids are called
aerostatic bearing linear compressors. Said compressors are endowed
with a more efficient lubrication system than the lubrication
system of the bearing compressors with viscous fluids due to the
lower viscous attribution coefficient of the gaseous fluid in
relation to the viscous fluid (oil). Another advantage of the
linear aerostatic compressor refers to the absence of an oil pump
to distribute the viscous fluid inside the compressor, a fact that
decreases the manufacturing cost and complexity of this
product.
[0007] An important characteristic of aerostatic bearing linear
compressors, hereinafter referred to as aerostatic compressors,
refers to the fact that they can have bearing formation through the
gas from the cooling fluid itself. As they have bearing by the very
cooling fluid that circulates through the compressor, this
equipment saves on an extra source of lubricant, since all the
lubricating fluid necessary for using these compressors is already
abundantly available inside them.
[0008] The aerostatic bearing compressor with cooling fluid is
endowed with bearing channels, located on the outer face of the
cylinder. These channels are capable of distributing the gaseous
fluid to distribution orifices which are spread along the cylinder.
The distribution orifices cross through the structure of the
cylinder, meeting up with the piston region, transporting gaseous
fluid homogenously to the gap existing between the cylinder and the
piston.
[0009] So that the gaseous fluid is uniformly distributed in the
gap between the piston and the cylinder, it is necessary to seal
the bearing channels, preventing communication between them and the
pressurized fluid outlet which will work in the bearing formation
of the piston.
[0010] Usually, the part that fulfills the function of sealing the
bearing channels is a metal jacket having tubular geometry,
referred to hereinafter as sealing jacket.
[0011] It is noted that between the inner surface of the sealing
jacket and the outer surface of the cylinder there may be gaps
which besides allowing undesirable communication between the
bearing channels, may increase the sectional area of certain
restriction channels, whereby causing a greater flow of fluid in
these channels and, consequently, lead to poor fluid distribution
in the gap between piston and cylinder, resulting in irregular
bearing formation.
[0012] For effective sealing of the restriction channels, it is
necessary to carry out interference coupling between the sealing
jacket and the cylinder, usually made of metal material. Besides
this operation, it is also necessary to carry out fine surface
finishing with a view to obtaining a surface endowed with low
roughness both on the outer face of the cylinder and on the inner
face of the jacket.
[0013] However, a fine surface finishing requires a size tolerance
that adds cost and increases the manufacturing time of these parts
due to the frequent need of turning and grinding processes on both
the parts.
[0014] Moreover, there is the drawback that interference coupling
between the sealing jacket and the cylinder may deform the cylinder
whereby characterizing another drawback to the arrangement of
jackets in aerostatic compressors of the state of the art.
[0015] A sealing jacket of aerostatic compressors of the state of
the art, such as the one mentioned, is made of metal material, that
is, a material having low flexibility, which requires a thorough
surface finishing so that it is capable of sealing the bearing
channels of the compressor.
[0016] Nevertheless, even if a thorough job is performed in the
manufacture of the sealing jacket and cylinder of the compressor,
there is still the possibility that flaws may arise in the end
product due to poor distribution of fluid between the piston and
the cylinder, which may decrease the yield of the compressor and/or
damage its internal parts, whereby decreasing its useful life. This
occurs because the metal constitution of the sealing jacket and of
the cylinder of the compressor prevent a perfect sealing of the
restriction channels, even if various machining and grinding
operations are carried out on these parts with a view to achieving
greater precision in the surface finishing of these components.
[0017] Therefore, there is still no sealing jacket of an aerostatic
linear compressor that decreases the complexity and cost of the
manufacturing process of this equipment, efficiently guaranteeing
the sealing of the bearing channels and that prevents the
occurrence of flaws arising from the interference coupling process
between the parts of the compressor.
Objectives of the invention
[0018] The objective of the present invention is to provide a
sealing system of bearing channels of aerostatic linear compressors
that is simple, efficient and capable of reducing production costs
of aerostatic linear compressors.
[0019] Another objective of the present invention is to provide a
sealing glove of restriction channels of aerostatic linear
compressors, the flexibility of which allows the sealing of
restriction channels in aerostatic compressors, whereby preventing
gas from escaping between the restriction channels.
[0020] A further objective of the present invention is to provide a
cooling system or appliance, endowed with said sealing glove.
BRIEF DESCRIPTION OF THE INVENTION
[0021] The objectives of the present invention are achieved by a
sealing glove for a cylinder of a linear compressor de aerostatic
bearing, the cylinder being defined by an outer surface and an
inner surface, the inner surface defining a through cavity inside
the cylinder, capable of enabling linear movement of a piston on
its inside, wherein the inner surface of the cylinder comprises a
plurality of distribution orifices which communicate with the outer
surface, the outer surface comprising bearing channels capable of
communicating with said distribution orifices, the glove being
flexible and disposed on the outer surface of the cylinder under
radial tension, the association between the outer surface and the
sealing glove defining bearing formation ducts capable of directing
the bearing fluid to the distribution orifices.
[0022] The objectives of the present invention are also achieved by
an aerostatic bearing linear compressor comprising a cylinder
defined by an outer surface and an inner surface, the inner surface
defining a through cavity inside the cylinder capable of enabling a
linear movement of a piston in its inside, wherein the inner
surface of the cylinder comprises a plurality of distribution
orifices which communicate with the outer surface, the outer
surface comprising bearing channels which communicate with said
distribution orifices, and a sealing glove is disposed on the outer
surface of the cylinder under radial tension, the association
between the outer surface and the sealing glove defining
restriction ducts capable of directing the bearing fluid to the
distribution orifices at appropriate pressure and in the adequate
quantity.
[0023] Lastly, an objective of the present invention is to provide
a cooling appliance which comprises a sealing glove as defined
above.
SUMMARY DESCRIPTION OF THE DRAWINGS
[0024] The present invention shall now be described in greater
detail based on an example of an embodiment represented in the
drawings. The drawings show:
[0025] FIG. 1--is a longitudinal cut view of an aerostatic linear
compressor of the present invention endowed with the flexible
sealing glove of the present invention;
[0026] FIG. 2--is a cross-sectional view of a flexible sealing
glove of the present invention positioned on a cylinder of an
aerostatic linear compressor;
[0027] FIG. 3--is a perspective view of a cylinder of an aerostatic
linear compressor of the present invention;
[0028] FIG. 4--is a perspective view of a cylinder of an aerostatic
linear compressor endowed with a flexible sealing glove of the
present invention;
[0029] FIG. 5--is a cross-sectional view of the BB section of an
aerostatic compressor linear endowed with a glove of the present
invention;
[0030] FIG. 6--is a cross-sectional view of a flexible sealing
glove of the present invention;
[0031] FIG. 7--is a cross-sectional view of a flexible sealing
glove of the present invention showing one of the potential effects
of internal pressure on the bearing channels;
[0032] FIG. 8--is a cross-sectional view of a flexible sealing
glove of the present invention showing one of the potential effects
of internal pressure on the bearing channels in light of the
external pressure to the flexible glove;
[0033] FIG. 9--is a longitudinal cut view of an aerostatic linear
compressor illustrating its working during the suction stage;
[0034] FIG. 10--is a longitudinal cut view of an aerostatic linear
compressor illustrating its working during the compression
stage;
[0035] FIG. 11--is a longitudinal cut view of an aerostatic linear
compressor illustrating its working during the exhaust stage;
[0036] FIG. 12--is a longitudinal cut view of part of the
compressor of the present invention in an alternative arrangement
illustrating an interface region;
[0037] FIG. 13--is a perspective view of a first alternative
arrangement of the cylinder of the compressor of the present
invention;
[0038] FIG. 14--is a perspective view of a second alternative
arrangement of the cylinder of the compressor of the present
invention; and
[0039] FIG. 15--is a perspective view of a third alternative
arrangement of the cylinder of the compressor of the present
invention.
DETAILED DESCRIPTION OF THE DRAWINGS
[0040] The main elements that make up an aerostatic linear
compressor 200 capable of receiving the sealing glove 100 of the
present invention, as can be noted in FIG. 1, are comprised by a
piston 15, having the function of carrying out an oscillatory
movement inside a cylinder 14; a cylinder 14 (see FIG. 3) endowed
with distribution orifices 3, connected to bearing channels 1,2,
(located on the outer face 5 of said cylinder 14); an outer block
13, capable of sealing the entire radial area of the compressor
200; a sealing lid 11, capable of sealing the forward face of the
compressor 200; a head 10 whose function is to separate the
compression chamber 12 (comprising the space between piston 15 and
cylinder 14) from the region prior to the sealing lid 11, which, in
turn, is comprised by the exhaust 11c and inlet 11a chambers
(separated by a division 11b); and a movement rod 16, capable of
transferring an oscillatory, linear movement from an external
source (not illustrated in the drawings) of the piston 15.
[0041] So that the piston 15, of the aerostatic compressor 200 of
the present invention has bearing in the contact region between
cylinder 14 and piston 15, it is necessary that under the inner
surface 4 of the cylinder 14 there be a layer of fluid preferably
gaseous that reduces the attrition between these parts, decreasing
the abrasion between them and increasing the yield of the
compressor 200. Notably, the present invention has application in
aerostatic compressors 200 which use the cooling fluid itself to
perform the bearing function.
[0042] The provision of this fluid layer, capable of bearing the
piston 15 inside the cylinder 14 of an aerostatic compressor 200
can be better understood by way of FIGS. 9, 10 and 11, which
illustrate the main stages of working of the compressor 200: [0043]
i--FIG. 9 illustrates the suction (or inlet) stage, where the
cooling fluid penetrates through the inlet tube 8, then fills the
plenum chamber 11a and finally occupies the compression chamber 12.
This occurs when the piston 15 moves in an opposite direction to
the sealing lid 11 and the inlet valve 7 is opened. [0044] ii--FIG.
10 illustrates the compression stage, which occurs when the inlet
valve 7 closes and the cooling fluid is compressed inside the
compression chamber 12, through a linear movement of the cylinder
towards the sealing lid 11. [0045] iii--FIG. 11 illustrates the
exhaust stage where the piston continues compressing the cooling
fluid inside the compression chamber 12 until its pressure exceeds
the pressure needed to open the exhaust valve 6 and this fluid may
be released to the exhaust chamber 11c. From the exhaust chamber
11c the fluid divides into two portions which follow two different
paths.
[0046] The major part of the fluid which enters the exhaust chamber
11c, returns to the cooling cycle of the cooling system where the
compressor 200 is inserted, through the exhaust tube 9; a second
portion of fluid, the portion which filled the exhaust chamber 11c
and did not return to the cooling cycle, follows a third cycle (a
cycle present only in aerostatic linear compressors 200 that use
the very cooling fluid to carry out the function of bearing
formation of the piston 15).
[0047] This second portion of fluid penetrates into a passage 10c,
located on a header 10 and then follows bearing channels 1,2, which
direct this fluid to distribution orifices 3 which, in turn, have
the function of providing a chamber of gaseous fluid between the
inner surface 4 of the cylinder 14 and the outer surface of the
piston 15.
[0048] As described, the compressor 200 of the present invention is
endowed with bearing channels 1,2, located on the outer surface 5
of the cylinder 14, whose function is to distribute (and restrict)
fluid to distribution orifices 3, which, in turn, pass on this
fluid to the gap existing between piston 15 and cylinder 14.
[0049] The bearing channels 1,2, may present various forms and
different arrangements, and may track different paths on the outer
surface 5 of the cylinder 14, such as, for example, along radial,
longitudinal, helical, diagonal paths, a combination between these
or any other capable of adequately performing the function (see
FIGS. 13,14,15). The sectional areas of these bearing channels 1,2
may also present various different forms such as, a triangular,
quadrangular, rounded geometry, among others. The bearing channels
1,2 can also be divided into feeder channels 2 and restriction
channels 1, such as illustrated in a preferred arrangement in FIG.
3.
[0050] The feeder channels 2 are commonly disposed in longitudinal
profiles along the cylinder 14 (see FIG. 3) and usually present a
sectional area having greater amplitude than the sectional area of
the restriction channels 1. Said characteristic is due to the fact
that the function of the feeder channels 2 is just to distribute
fluid to the restriction channels 1. The restriction channels 1
also comprise the function of regulating the pressure of the fluid
before it is displaced to the gap between piston 15 and cylinder
14. The restriction channels 1, in turn, are distributed in a
radial arrangement along the outer face of the cylinder 14, and
usually have the capacity to communicate directly with distribution
orifices 3 that release bearing fluid to the gap between piston 15
and cylinder 14.
[0051] So that these bearing channels 1,2 effectively fulfill the
function of distributing bearing fluid in a uniform manner to the
distribution orifices 3, it is necessary that these channels 1,2
are sealed by some type of outer surface of the cylinder 14 that is
capable of preventing the flow of fluid of a certain channel 1,2
from leaking to a neighboring channel 1,2.
[0052] This sealing surface, when overlapping the channels bearing
formation 1,2, define bearing formation ducts 1',2'. The bearing
formation ducts 1',2', by presenting a closed structure
(differently to the bearing channels 1,2), are effectively capable
of providing fluid to the distribution orifices 3 without this
fluid leaking from one channel 1,2 to the other channel 1,2.
[0053] Therefore, the present invention is focused on sealing these
bearing channels 1,2 through the disposition of a flexible sealing
glove 100 on the outer face 5 of the cylinder 4, such that the
sealing glove 100 maintains the cylinder 14 under radial
compression. Put otherwise, the sealing glove 100 of the present
invention can be defined as a substantially tubular object, having
a flexible/elastic constitution capable of providing the sealing of
the bearing channels 1,2 through a radial tension which maintains
its structure in contact with the outer surface 5 of the cylinder
14 (see FIGS. 4 and 5).
[0054] The sealing glove 100 of the present invention is made of a
substantially polymeric material, that is, a material that may
comprise composites, polymers, elastomers and any other materials
endowed with organic substances, which have average or high
flexibility and which have an elasticity limit capable of enabling
this sealing glove 100 to be fastened to the cylinder 14, under
radial tension, preventing the presence of gaps between the glove
100 and the cylinder 14. Furthermore, it has to be noted that for
this radial tension to occur, it is also necessary for the inner
diameter of the glove 100, when it is not tensioned, to be slightly
less than the outer diameter of the cylinder 14, whereby enabling a
tensioning of the glove 100 material on the outer surface of the
cylinder 14.
[0055] In another preferred arrangement, it is possible for the
inner diameter of the sealing glove 100 to present, before being
applied to the cylinder 14, an inner diameter that is greater than
the outer diameter of the cylinder 14. In these cases, the glove
100 may be made of a thermo-contractile material, that is, a
material which, once heated, contracts so as to permit installation
with a tight adjustment of the sealing glove 100 on the cylinder
14.
[0056] As described, the glove 100 has benefits such as better
sealing of the bearing channels 1,2 due to a radial tensioning of
its structure around the cylinder 14, being capable of eliminating
the gaps existing between the glove 100 and the outer surface 5 of
the cylinder 14, whereby improving the process of bearing formation
of the piston 15 inside the compressor 200.
[0057] However, the flexibility of the glove 100 may potentially
cause a drawback to the working of the compressor 200. Said
flexibility allows the glove 100 to bend oppositely to its axial
center `X` in the regions comprised over the bearing channels 1,2,
(as can be noted in FIG. 7) due to the fact that the pressure
existing on the bearing formation ducts 1',2' is greater than the
pressure on the outer side of the glove.
[0058] Yet this potential problem is solved by applying a positive
pressure to the interface region 17 defined between the outer face
of the sealing glove 100 and the inner face of the outer block 13.
Said positive pressure, when operating on the outer face of the
glove 100, neutralizes the force exerted by the positive pressure
acting under the inner face of the glove 100 (see FIG. 6). This
extra source of positive pressure is exerted by the cooling fluid
existing on the exhaust chamber 11c which may act not only on the
inner face of the glove 100 (running through the bearing formation
ducts 1',2') but also on the outer face of the glove 100, exerting
a counter pressure to the pressure existing on the bearing
formation ducts 1',2', whereby guaranteeing a constant flow in the
bearing formation ducts 1',2' (see FIG. 12).
[0059] In short, when its outer face is exposed to a pressure equal
to the discharge pressure of the compressor 200, the flexible
sealing glove 100 becomes capable of sealing the bearing channels
1,2, with greater effectiveness so as to avoid the leakage of fluid
between said bearing channels 1,2.
[0060] However, even using a flexible sealing glove 100 and a
positive pressure acting on its outer face, a third problem may
still occur in the compressor 200. If the pressure acting on the
outer face of the glove 100 is slightly greater than the pressure
acting inside the bearing formation ducts 1' and 2', the sealing
glove 100 may bend slightly towards the central reference axis `X`
(see FIG. 8). Nevertheless, this problem can be solved by an
oversizing in the section of the bearing channels 1 and 2 or even
by altering the composition and/or diameter of the sealing glove
100.
[0061] It is obvious that the linear aerostatic compressor 200 as
well as the flexible sealing glove 100 of the present invention may
comprise various constructive alternatives, related to different
forms, materials and dispositions, provided that all these
alternatives comprise the conceptual part of this invention, as
disclosed in this specification.
[0062] Below are some alternative embodiment possibilities of the
present invention: [0063] i. The flexible sealing glove 100 of the
present invention may be made of: rubber, polyethylene, PVC among
other polymers or composites, provided that they are capable of, at
least, providing flexibility to its structure. The surface
finishing of this 100, may be smooth or rough or even a composition
in which different parts of the glove 100 present different surface
finishings. Regarding its physical shape, the glove 100 of the
present invention may present sealing rings at its longitudinal
ends capable of retaining the glove 100 fastened in an axial
positioning on the cylinder 14, as well as holes corresponding to
protrusions in the cylinder 14 also endowed with the function of
retaining the glove 100 in a fastened positioning inside the
compressor 200. Further in regard to its composition material, the
glove 100 may present a mixture of elements in its structure, such
as, for example, the combination of a polymer and a nylon mesh that
guarantees greater resistance to its structure (such as used in
tires) or the incorporation of metal rings in its structure that
prevent radial flexing oppositely to the axial center `X` of the
compressor 200. In terms of its function, the glove 100 may be
capable of flexing inwardly of the bearing channels 1,2 bending
slightly under an external pressure, or may be endowed with an
elasticity coefficient such that it is capable of resisting an
internal pressure of the bearing formation ducts 1',2' keeping the
sectional area of the bearing formation ducts 1',2' constant.
[0064] ii. The fluid capable of pressurizing the outer face of the
glove 100 against the cylinder 14 may be provided through channels
or orifices located on the inner face of the outer block 13 or may
be freely distributed on the interface 17 between glove 100 and
outer block 13. [0065] iii. The cylinder 14, besides being able to
comprise bearing channels 1,2 in different arrangements on its
outer face, such as previously described, may also be comprised of
different materials, such as metal polymers and composites, porous
or not, provided they allow suitable running of the compressor
200.
[0066] Note that the alternative arrangements disclosed above are
merely illustrative alternatives of countless possibilities that
the present invention may comprise. It is also noted that the
alternative arrangements both of the flexible sealing glove 100 and
the compressor 200 of the present invention are not exhausted in
this specification, and may comprise innumerous alterations,
provided that they all comprise the conceptual part of the present
invention.
[0067] Lastly, regarding the benefits achieved by the present
invention, it can be said that the new arrangement of this glove
100 has benefits both in terms of the manufacturing process of the
compressor 200, and in the utilization itself. In relation to the
manufacturing process of the compressor 200, this polymeric sealing
glove 100 dispenses with the need to perform rigorous processes on
the surface finishing of the inner face of the glove 100, and on
the surface finishing of the outer face of the cylinder 14. The
elimination of such processes reduces costs, time and the
complexity of production.
[0068] As for utilization of the compressor 200, it can be seen
that this new technology increases its efficiency and its yield.
Said attributions originate from the reduction of gaps between the
sealing glove 100 and the cylinder 14 that are so common in the
state of the art; the decreased risk of operating failures in the
compressor 200 (since the compressor 200 that uses this new
technique has a lower risk of presenting malfunctions because it
does not have cracks and internal deformations arising from
interference coupling between the glove 100 and the cylinder 14);
and, lastly, owing to improved distribution of bearing fluid in the
gap between piston 15 and cylinder 14 thanks to the elimination of
leakage between the bearing formation ducts 1',2' of the compressor
200 along its extensions.
[0069] Lastly, it is noted that a compressor 200 containing the
glove 100 as described may, among the most diverse applications, be
used in the cooling industry.
[0070] Having described an example of a preferred embodiment, it
should be understood that the scope of the present invention
encompasses other possible variations, being limited only by the
content of the accompanying claims, potential equivalents being
included therein.
* * * * *