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Патент USA US2134782

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Nov. 1, 1938.
w, FQuRNEss
2,134,782
REG IPROCA'I'ING COMPRESSOR
Filed April 16, 1954
3 Sheets-Sheet 2
57
.56
INVENTOR
I/VI/ra" F rness
BY
‘
‘
'
ATTORNEY
>
NOV. 1, 1938.
'
w_ FOURNESS
'
2,134,782
REC I PROCATING COMPRES SOB
Filed April 16, 19254 '
Ti?‘ 5:72 ‘/
5 Sheets-Sheet 3
I
7
I
- ‘
\NVENTOR
I/V/Yf'
Fa r'nass
{5% M
ATTORN E V
Patented Nov. 1, 1938
I
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Y
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UNITED STATES PATENT OFFICE
2,134,782
RECIPROCATING COMPRESSOR
Wilfred Foumess, Oakland, Calif” assignor, by
mesne assignments, to Fourness Development
Corporation, Ltd.
Application April-16, 1934, Serial No. 720,888
11 Claims.‘ (01. 230-192)
This invention relates to a compressor mecha-
contemplates the use of a combination of intake
nism, and especially to one to be used in connec-
means. - One of these is a suction valve open dur
tion with refrigerating systems. In systems 0!
ing the suction stroke; and the other of these is
that character, it is now- common to provide a
5, fluid refrigerant medium, which can be vaporized,
as in an expansion coil, and then it is passed to a
compressor to be compressed; and the compressed
vapor is then condensed into liquid form. During vaporization, there is a corresponding absorp10 ‘tion of heat. The cycle of evaporation, compression, and condensation, is repeated until the temperature at or near the expansion coil is reduced
to a desired value.
'
.
opened only at the end of the suction or intake
vstroke, to provide a ?ash intake, supplementing 5
the action of the suction valve.
It is still another object of the invention to pro
vide a simple and effective lubricating system and
oil seal for the cylinder and piston and their asso
elated reciprocating mechanism.
10
This; invention possesses many other advan
tages, and has other objects which may be made
more easily apparent from a consideration of one
Since the use of mechanical compressors in ‘embodiment of the invention. For this purpose
15 such systems is now well understood, further de- there is shown a form in the drawings accom- 15
scription thereof is unnecessary.
.
panying and forming part of the present speci
It is one of the objects of this invention to im- ?catio'n. This form will now be described in de
prove in general, reciprocating compressors for tail, illustrating the general principles of the in
gaseous or vaporous media.
vention; but it is to be understood that this de
20
In mechanisms of this character, it is impor- . tailed description is not to be taken in a limiting 20
tant and advantageous to keep the size and sense, since the scope of the invention is best
weight of the compressor to as low a value as pos-
de?ned by the appended claims.
sible, and yet maintain adequate capacity of the
Referring to the drawings!
system.
Figure 1 i8 8 Side elevation 01 a compressor em
One factor toward accomplishing this
25 result is that of high speed operation. This'high
speed operation however, introduces further
problems in the construction of the compressor.
By the aid of this invention, high speed operation of a reciprocating type of compressor is
bodying the invention, the end cover being 25
removed, and the right hand cylinder as well as a
portion of the associated parts being shown in
section;
Fig. 2 is a sectional view of the compressor
30 rendered highly e?‘icient, and it is- accordingly an-
taken along plane 2—2 of Fig. 1;
other object of this invention to make it possible
‘
‘
30 -
Fig. 3 is a detail sectional view, taken along .
to operate et?ciently a reciprocating compressor
plane 3-8 of Fig. 1;
at speeds as high as 1800 revolutions per minute.
Such speeds are especially advantageous, since
Fig. 4 is a fragmentary side elevation of a yoke
utilized in connection with the reciprocating
35 electric motors, operating from sixty cycle alterhating currentmains, are also capable of e?ici'ent operation at equivalent speeds. The invention however is not limited to high speed com-
pressors, as it may be used quite effectively for
40 lower speeds.
I
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mechanism;
35
Fig. 5 is a sectional view, taken along plane 5-5
oi‘Fig. 2, but with a portion of the oil disc broken
away; ‘
Fig. 6 is a detail section of the right hand cylin
der and piston, showing the positions of the valves 40
The compressor can be built with one or more
at an intermediate position of the suction or
sets of cylinders and pistons. At the high speed
of operation speci?ed, it is apparent that the cylinder space during the intake phase of the cycle
intake stroke;
Fig. 7 is a detail view of the right hand cylinder
and piston, showing the positions of the valves
45 should be ?lled with as much of the medium as
possible; and. it is also highly advantageous to
ensure that the discharge port stays open only
during the actual discharge period, so as to pre-
vent any back ?ow of the compressed medium
50 upon beginning of the intake stroke. It is another object of this invention to provide a valve
structure for high speed operation, that makes it
possible to attain these results.
In order to facilitate the ?lling of the cylinder
55 chamber during the intake stroke, the invention
at the end of the suction‘ or intake stroke;
45
Fig. 81s a detail section of the right hand cylin
der and piston, showing the positions of the valves
at an intermediate position of the compression ‘
stroke;
Fig. 9 is a view similar to Fig. 8, but showing 50
the positions of the’ valves at or near the end
of the compression stroke;
'
a
Fig. 10 is a rear view of the discharge valve
closure; and
Fig. 11 is an end view of one of the pistons, the 55
2
2,184,782
suction valve closure being partly broken away.
In the present instance, a pair of cylinder
blocks i and 2 as well as a corresponding pair of
pistons 3 and 4 are provided.
These pistons and
blocks are coaxial, and can be arranged in op
posed relation with respect to a supporting inter
mediate casing 5 (Figs. 1, 2, 5). In order to hold.
the blocks I, 2 to the casing 5, each of these
blocks can be provided with an intermediate
?ange 6 or 1 (Figs. 1 and 6), respectively cooper
ating with bosses 8 and 3 on the sides of the
casing 5. The inner ends of each block‘ I, 2 can be
accommodated in apertures formed in casing 5,
and bolts such as It can be used for tightening
15 ?anges 5, 1 against bosses 3, 9 in a ?uid tight
manner; if necessary, by the aid of gaskets.
Since both of the cylinder blocks i, 2 and pis
tons 3, l are of substantially identical construc
tion, only cylinder block I and piston 3 will be
20 described in detail. The cylinder block i has
external annular cooling ?ns H (Figs. 1 and 6).
The outer end of the cylinder block i is closed by
a cylinder head H’, the construction of which is
shown to best advantage in Fig. 6. This .head
25 telescopes over the beveled end of the block 1, and
is attached to the ?ange l2 as by cap screws IS.
A chamber I3’ is formed intermediate the end
wall of head H’ and the corresponding end of
the block 1. Into this chamber the compressed
refrigerant is permitted to pass during the end
portion of the compression stroke. The’ valve
mechanism to accomplish this result will be here
inafter described. It is here sufficient to note
that the head II’ has a tapped hole H into which
35 a pipe elbow l5 can be screwed.
A pipe connec
tion It (Fig. 2) extends from elbow [5 into one
which is to the left of the enlargement 2|. This
portion 29 is preferably provided with a plurality
of annular oil grooves 30 to carry oil into the
cylinder bore from the interior of casing 5, where
by the oil serves not only as a lubricant but also
as a liquid seal for the cylinder bore.
The piston proper 3 is located at the outer end.
and engages that portion of the cylinder bore
which is to the right of the enlargement.2 l.
Be
tween portions 29 and 3 is a. reduced portion 3E, 10
formed by beveled or conical surfaces 32, 33.
In
the present instance, the intake valve structure
is incorporated with the piston 3. Thus there
are a plurality of apertures or passageways 32!,
having axes parallel to the axis of the piston 3,
and having centers falling on a circle having its
center on the axis of the piston. These passage
ways extend entirely through the piston 3, ‘so
that gaseous or vapor medium to be compressed
can pass through them from the enlarged bore 20
2E, to the cylinder chamber 35.
A closure 36 in the form of a disc is adapted
to close the apertures 34, but moves away to
uncover these apertures during the'suction stroke.
The direction of the suction stroke is indicated
by arrow 3? in Fig. 6. The valve closure 36 is
arranged to be accommodated in a shallow re
cess38 in the end of the piston 3. It is further
more guided and limited in its axial movement
by the aid of a central post 39. This post has a
threaded reduced part 40 engaging in a threaded
central aperture in piston 3. A set screw M?
can be used to lock post 39 in place. The inner
end 4| of the unthreaded portion engages snugly
against a corresponding shoulder around the
threaded central aperture. The post 39 passes
of the upper corners of the casing 5, thus carry
ing the compressed medium into the casing. The
through the valve closure 36 and has a head. 42
for limiting the motion‘ of closure‘ 36 from the
interior of casing 5 is thus maintained at dis- . closed position of Fig. 8.
40 charge pressure. The pipe connection I‘! (Fig. 1)
The distance through which the closure 38 is 40
serves correspondingly to lead the compressed permitted to move to uncover the ports or pas
medium from the cylinder block 2 into the eas
sages 33 can be quite short, since even a short
ing 5.
The compressed medium in casing 5 is with
45 drawn therefrom as needed, through an oil and
gas separator l8 (Figs. 1 and 2), and through
the outlet pipe l9. Separator l8 can be of any
convenient fonn, and can be provided, if desired,
with appropriate screening and draining ele
ments.
It serves to prevent any substantial
amount of lubricant from passing out of casing 5,
said lubricant forming a pool in the bottom of
the casing and serving to lubricate the moving
parts in a manner to be hereinafter described.
The intake for the cylinder block I is provided
by atapped hole 20 (Figs. 6, 7, 8 and 9) , leading
to an enlarged portion 2| of the cylinder bore,
forming an inlet chamber. An elbow 22 connects
to the inlet aperture 20, and a pipe connection 23
60 connects elbow 22 to the source of the medium
55
to be compressed. A pipe connection 24 serves a
similar purpose for block 2. For convenience,
both pipes 23 and 24 can lead to opposite arms
of a common four-way connector 25 (Fig. 2).
65 One of the remaining arms can connect to a
common inlet pipe 26; and the last arm can be
plugged by a screw member 21, fastened into a
boss 28 on casing 5. Thus member 21 can con
veniently serve as a support for the inlet con
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70 nections.
The construction of the piston member 3 can
be best described in connection with Figs. 1 and 6.
The piston can conveniently be termed a double
trunk piston, the~inner portion 23 serving as a
guiding stem in that portion of the cylinder bore
movement can provide a rather wide annular pas
sageway around the edge of closure 36 for the
intake gases. The passage of the gases during 45
intermediate portions of the intake stroke is indi
cated by arrows 43 in Fig. 6. Thelaxial separation
of closure 36 from the cooperating surface of
piston 3 can be in fact as small as three-sixty
fourths of an inch.
Such small valve movements are especially use
60
~i'ul with high speed reciprocating mechanisms,
since very little time is taken up to produce full
opening when the suction stroke begins. Fur
thermore, the carrying of the suction valve clo
sure 36 on a post 39 supported on the piston
also assists in rapid valve opening. Just as soon
as piston 3 reverses at the end of its compression
stroke (illustrated in Fig. 9), the inertia of clo
sure 36 acts to cause it to move, relative to piston 60
3, to the open position.
During the entire suction stroke, the apertures
34 are thus uncovered, and the gases or vapors
to be compressed can enter into chamber 35.
However, since the speed of the compressor is
quite high, such gases may comprise less than
the weight which the compressor can effectively
compress in a cycle. Accordingly, a supplemental
intake is provided, which is effective just pre
ceding the end of the suction stroke.
This result is accomplished by placing the
chamber 35 in direct communication with the
enlarged portion 2| of the bore, by passing piston
3 completely out of the chamber 35. This posi
tion is shown in Fig. 7. Here the intake can 76
3
2,134,782
occur past the edge of piston 3, from portion 3|,
directly into chamber 35. There is thus formed
a narrow annular passageway between portion I2
and chamber 35; and although it is narrow, yet it
extends entirely around the periphery of piston
is shown in Fig. 8.
'
The gases and vapors are thus free to fill
Should any oil or other foreign matter be
the whole chamber 35 just before the compression
trapped in the cylinder space 35, the valve 46 is
3.
forced open by it as soon as the space 35 is re
stroke. '
The supplementing of the intake openings 34
10 in this manner is of considerable importance in
increasing thé efficiency of the mechanism; and
this is especially the case when the speed of the
compressor is high.
The inertia of the closure 36 also assists in
15 hastening the closing of the intake passages 34
immediately upon the beginning of the compres
sion stroke. The direction of the compression
stroke is indicated by arrow 45 at the lower por
tion of Fig. 8. Just as the piston 3 reverses its
20 motion and starts to move in the direction of
arrow 3, closure 36 is immediately seated. The
advancing edge of piston 3 also closes the left
hand end of chamber 35, so that the charge of
gas and vapor in in this chamber is now subjected
25
and of the outlet pressure in chamber I3’, valve
46 lifts, and the compressed gases can flow
through slots 5| into chamber I3’, ‘and out
through aperature I4 and elbow I5. This position
to compression.
_ ‘
Upon su?icient movement of piston 3 to the
right, the pressure in chamber 35 becomes suffi
ciently great to open a discharge valve, the struc
ture of which will now be described. The entire
30 right hand end of chamber 35 is arranged to be
duced to that of the body of oil or foreign matter.
The valve 46 opens widely and the oil is quickly
ejected without any material stresses being
created in the mechanism.
This description of the compression operation
applies equally well to the operation of the piston
structure 4 in the cylinder block 2.
15
Both of the coaxial piston structures 3, 4, can
be reciprocated by a common mechanism.
As
shown most clearly in Figs. 1 and 2, casing 5 has
formed therein, an upper track 52 and a lower
track 53. These can be supported as by integral 20
legs 54, and each of them can be provided with a
vertical guide surface 55. Guided for movement
on the tracks 52, 53, and abutting the guide sur
faces 55, is a yoke structure 56. This yoke struc
ture is substantially rectangular in outline, its 25
upper and lower edges cooperating with the guides
and tracks. Its side members can be reinforced
as by ribs 51 and are respectively detachably
keyed to the inner ends of the piston structures.
In this way, reciprocation of the yoke 56 causes a 30
closed by a disc closure 46 (Figs. 6, '7, 8, 9, and 10)
corresponding reciprocation of the piston struc
guided in recess I3.
tures.
One way in which the keying between the
yoke 56 and the pistons can be accomplished is
indicated in Figs. 3 and 4. Each of the inner 35
ends of the piston structures 3, 4 carries a projec
tion 53 that has an enlarged head 59. The yoke
structure 56 carries at each side a slotted mem
ber 60, the slot 6I thereof being disposed in a
This closure is urged toward
closing position by the discharge pressure ef
fective on its face, in chamber I3; but this clos
35 ing action can be supplemented by a compression
spring 41. One end of this spring abuts against
the end wall 48 of the hollow spring housing 49.
This‘housing is formed integral with the cylinder
head II’. The other end of spring 41 encircles
40 a boss 50 on the closure 46.
Upon suflicient pressure being attained in
chamber 35 during the latter part of the com
pression stroke, the closure 46 is lifted against
the action of spring 41 and of the outlet pressure.
45 The compressed gases then pass through the slots
5| (Fig. 10) in the periphery of closure 46, into
chamber I3 and thence outwardly through port
I4 and elbow I5. Spring 41 is just strong enough
to prevent too wide an opening of closure 46.
It
50 is also to be noted that the head 42 of post 33
can enter a corresponding recess in the closure 46
at the end of the compression stroke.
A complete cycle of operations for one cylinder
and its piston can now be summarized.
At the
55 beginning of the suction stroke, the piston 3 is in
the position of Fig. 9, and is moving toward the
left. Closure 46 closes the end of cylinder block I.
Due to the rapid reversal of the piston travel,
closure 36 by inertia, opens very quickly. The
60 valve positions are then as shown in Fig. 6.
The medium to be compressed enters chamber 36
throughout
substantially ‘the
entire suction
stroke, via elbow 22, aperture 26, chamber 2I, and
apertures 34. At and near the end of the suction
stroke, the medium to be compressed can also
pass around the peripheral edge of the piston 3 di
rectly from. chamber 2I into chamber 35. This
condition is illustrated in Fig. 7 .
I
Directly upon reversal of movement of piston 3
70 to begin its compression stroke, the'valve closure
36 is moved by inertia to closing position. It stays
closed thereafter until the compression stroke is
completed. Upon the arrival of the piston 3 to a
position where the gas pressure in chamber 35
can overcome the combined action of spring 41
horizontal direction and being just wide enough
to engage the projection 58 beneath the head 59.
In this way, the yoke structure 56 can be slid into
place from the right of casing 5 as viewed in Fig.
2, slots 6| being immediately engageable over the
projections 58.
‘In order to reciprocate yoke structure 56 on
tracks 52, 53 in a horizontal direction, an eccentric
block 62 is provided. This block is arranged to
slide vertically inside the yoke 56 and along its
sides. As shown most clearly in Figs. 1 and 3, 50
it has extending vertical edges 63 overlying the
yoke sides and serving to con?ne the yoke struc
ture 56 against movement off the guiding tracks.
In order to move the block 62, an eccentric 64 is
provided, engaging a circular aperture in block 62. 55
The eccentric 64 is rotatable about an axis 65. In
fact, eccentric 64 can conveniently be formed in
tegrally with a driving shaft 66.
In order to hold block 62 against relative axial
movement, eccentric 64 can have a rear flange 61 60
engaging the rear edge of block 62; and a disc 68
can be fastened to the front face of the eccentric
62, and overlying the front edge of the block 62.
It is apparent, without further explanation,
that rotation of shaft 66 in either direction, will 65
cause block 62 to rise and fall in yoke 56, and at
the same time, yoke 56 will be reciprocated by the
block 62 in a horizontal direction. For balancing
purposes, a counterweight 69 can be used, integral
with shaft 66. If desired, however, this counter
weight can serve as an additional eccentric to
operate an additional pair of pistons; and of
course in general, as many eccentrics and yokes
can be accommodated in casing 5 as may be re
quired to increase the capacity of the compressor.
4
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In order to maintain casing 5 ?uid tight, so
that it may maintain the compressed gases passed
into it at the discharge pressure, the casing is
to the shaft axis as well as apertures transverse
closed at the front end by a cover 10, and at the
back end by a cover ‘ll. These covers are shown
passing lubricant into said transverse apertures.
as having ?anges overlying corresponding ?anges
10
on each side of the casing 5. Through the ?anges
pass a number of fastening screws 12. Further
more, each cover can be provided with appropriate
journals for supporting shaft 86.
,
Thus cover 10 is shown as having a boss 13
through which shaft 66 extends, for appropriate
connection to a source of power. A bearing sleeve
14 is inserted inside of boss 13. Provisions can
15 be made to prevent ?uid leaks around the ex
tending portion of shaft 66. For example, a cap
15 (Fig. 2) can be telescoped over the reduced end
of boss 18, and can be fastened thereto in a ?uid
tight manner as by cap screws 16. Shaft 66
20 passes through cap 15 with a running clearance.
However, a number of compressible or yielding
washers 11 can encircle the shaft 66 inside of boss
‘II, to form a ?uid tight fit with said shaft. These
washers can be held in a cup 18 abutting the in
25 ner surface of cap 15; and a compression spring
19 disposed over shaft 66 can be used to urge the
cup 18 and washers 11 against the cap 15.
If desired, a thrust ball bearing structure 80
can be provided between the cover 10 and the co
80 centric 64. This structure can serve to hold the
yoke 56, block 52 and shaft 56 in de?nite axial
position.
Cover ‘H can in general be designed in a man
ner similar to cover 10, to permit shaft 66 to pass
85 therethrough so that the compressor may be
driven from either end. However, in this in
stance, cover ‘H is shown as having a bearing
sleeve 8! inside of boss 82, which has a separable
cover 83.
(0
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In order to provide lubrication as well as an oil
seal, a body of lubricant 84 is formed in the
bottom of casing 5.
It can have a level such as
indicated at 85, which is about as high as the _
lower track guide 53. Oil is passed to the shaft
45 bearings and the pistons in a manner now to be
described. An oil disc 86 (Figs. 2 and 5), dips
into the oil 84 and carries some of it upwardly.
A rib 51 is formed on the inner side of cover ‘H,
having a. number of downwardly directed pas
Ni sageways 88. These openings are located on
each side of the rib 81, and they all lead into a
vcommon radial aperture 89. This aperture is
connected to passage 90 in boss 82.
Oil can pass
from this passage through groove 8| in cap 83,
From
this aperture, centrifugal force throws lubricant
through radial oiling apertures, such as 93, for
block 62; and 94, for journal ‘H. Oil of course
can pass to the rear bearing sleeve 8| via open
ing 95. To prevent any oil from being trapped
in boss 13, a diagonal passage 96 is provided from
the front end of the boss, into the casing 5.
55 into the long axial aperture 92 in shaft 56.
The disc 86 also throws oil on the exposed
parts of the piston structures, to provide an oil
65 seal as heretofore explained.
I claim:
1. In a compressor mechanism, a casing, a
piston and a cylinder structure supported by the
casing, means in the casing for causing relative
70 motion between the piston and the cylinder. in
cludinga shaft, said casing having a body of
lubricant therein, and means for distributing said
lubricant through the shaft to sliding parts of
the mechanism, including means independent of
ll the piston and shaft, forming an aperture radial
thereto and communicating therewith, the outer
ends of the apertures being open, and means for
2. The combination as set forth in claim 1, in
which the transverse apertures slant downwardly,
and in which the radial aperture communicates
with an axial aperture in the shaft.
3. In a reciprocating gas compressor, means
forming a cylinder space and a piston structure 10
operating in said space, said compressor having
an inlet valve adapted to open near the beginning
of the intake stroke and to close near the be
ginning of the compression stroke, said piston
structure having an annular surface which is
spaced from the walls of the cylinder space near
the end of the intake stroke to form an annular
inlet passageway supplemental to the inlet valve
and which closes near the beginning of the com
pression, stroke, and remains closed for the re 20
mainder of the stroke.
4. In a reciprocating gas compressor, means
forming a cylinder space and a piston structure
operating in said space, there being an enlarged
bore at one end of said space forming an in
take“ chamber, said structure having an inlet port,
23
a valve adapted to open said port near the be
ginning of the intake stroke and to close it near
the beginning of the compression stroke, said
structure having an annular surface which is 30
spaced from the walls of the cylinder space near
the end of the intake stroke to form a supplemen
tal annular inlet passageway which closes near
the beginning of the compression stroke, and
means whereby said inlet port is maintained con_ 85
tinuously in communication with said intake
chamber.
5. In a reciprocating gas compressor mecha
nism, a cylinder block having a bore forming a
cylinder, as well as an enlarged bore communi 40
cating with the cylinder bore, means forming an
inlet passageway to the enlarged bore, a piston
structure having a part reciprocating in the cyl
inder bore, as well as a coaxial guiding part, said
block forming a guideway for said coaxial part, 45
beyond the enlarged bore, forming a seal for the
cylinder, and means for so- reciprocating the
piston structure that the inner end thereof, at
the end of the intake stroke, passes out of the
cylinder bore, said piston structure having one 50
or more passageways forming an inlet port in
direct communication with the enlarged bore and
the interior of the cylinder, and a valve for con
trolling said passageways.
6. In a reciprocating gas compressor mecha
nism, a cylinder block having a pair of spaced
coaxial cylinder bores, joined by an intermediate
enlarged portion forming an inlet chamber,
means forming an inlet passageway to said
chamber, one of said cylinder bores forming a
compression space and the other of said cylinder
bores forming a guideway, a piston structure
having a. working end reciprocating in the com
pression space, as well as a coaxial guiding por
tion reciprocating in the guideway, said guiding 65
portion forming a seal with the guideway for the
compression space and the inlet chamber, and
means for so reciprocating the piston structure
that the working end thereof, at the end of the
intake stroke, passes out of the cylinder bore, 70
whereby the inlet chamber and the compression
space are placed in communication.
'7. In a reciprocating gas compressor mecha
nism, a cylinder block having a pair of spaced
coaxial cylinder bores, joined by an interme 76
5
2,184,782
diate enlarged portion forming an inlet cham
her, means forming an inlet passageway to said
chamber, one of said cylinder bores forming a
compression space and the other of said cylin
der bores forming a guideway, and a piston
structure having a working end reciprocating in
the compression space, as well as a coaxial guid
ing portion reciprocating in the guideway, said
guiding portion forming a seal with the guide
10 way for the compression space and the inlet
chamber, the axial length of said working end
being less than the axial length of the inlet
trol said passage, said-guiding portion forming
a seal with the guideway for the compression
space and the inlet chamber, the axial length
of said working end being less than the axial
length of ‘the inlet chamber, and means for so
reciprocating the piston structure that the work
ing end thereof at the end of the intake stroke
passes out of the compression space and into the
inlet chamber so as to be spaced from each end
thereof, whereby the inlet chamber is simulta 10
neously in communication with the compression
space and said passage.
_
1Q In a reciprocating gas compressor mecha
‘ chamber.
8. In a reciprocating gas compressor mecha nism, a cylinder block having a cylinder bore
15 nism, a cylinder block having a pair of spaced with an enlarged intermediate portion, whereby 15
coaxial cylinder bores, joined by an intermediate the bore is divided into a compression space and
enlarged portion forming an inlet chamber, ' a guideway, a double truck piston reciprocating
in said cylinder bore and having a working end
means forming an inlet passageway to said cham
cooperating with said compression space, said
ber, one of said cylinder bores forming a compres
20 sion space and the other of said cylinder bores working end being of less axial length than the
enlargedportion of the cylinder bore, and means
i'orming a guideway, and a piston structure hav-'
ing a working end reciprocating in the compres— for so reciprocating the piston that the working
sion space, as well as a coaxial guiding portion end of the piston is entirely within the enlarged
portion of the cylinder bore at the end of the
reciprocating in the guideway, said guiding por
25
25 tion forming a seal with the guideway for the stroke.
11. In a reciprocating gas compressor mecha
compression space'and the inlet chamber, the
axial length of said working end being less than nism, a cylinder block having a pair of spaced
the axial length of the inlet chamber, and means coaxial bores, joined by an enlarged intermediate
for so reciprocating the piston structure that the
30 working end thereof, at the end of the‘ intake
stroke, passes out of the compression space and
into the inlet chamber, so as to be spaced from
each end thereof and unsupported by the com
pression space.
35
>
9. In a reciprocating gas compressor ‘mecha
nism, a ‘cylinder block having a pair of spaced
coaxial cylinder bores, joined by an intermediate
enlarged portion forming an inlet chamber, means
forming an inlet passageway to said chamber, one
01 said cylinder bores forming a compression
40 space and the other of said cylinder bores form
ing a guideway, a piston structure having a work
ing end reciprocating in the compression space,
as well as a coaxial guiding portion reciprocating
in the guideway, there being an inlet passage ex
45 tending through the working end, a valve to con
‘chamber, means forming an inlet passage to said
chamber, one of said bores forming a compres 30
sion space and the other of said bores forming a
guideway, a piston structure having a working
end reciprocating in the compression space, as
well as a coaxial guiding portion reciprocating
in the guideway, said guiding portion forming a
seal with the guideway for the compression space
and the inlet chamber, and means for so recipro
eating the piston structure that the working end
thereof, near the end of the intake stroke, passes
out of the compression space, the piston struc
ture being entirely supported by the guideway,
the compression space being placed in commu
nication with the inlet chamber.
' WILFRED FOURNESS.
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