COMPRESSEURS A SIMPLE ET DOUBLE EXTREMITE

SINGLE AND DOUBLE-ENDED COMPRESSORS

Abrégé français

Cette invention se rapporte à un compresseur de réfrigérant à double extrémité (30) qui est constitué par une paire de compresseurs opposés (10a) comportant chacun un piston creux (14, 14a) mû par une armature (13, 13a) sous l'action de bobines électriques (12, 12a) de façon à comprimer le réfrigérant dans les chambres (15, 15a). Les armatures (13, 13a) comportent des déflecteurs d'huile (31) destinés à projeter l'huile du carter d'huile (17, 17a) vers les pistons (14, 14a) et vers les chambres (15, 15a). Un obturateur (41) peut être adapté sur l'extrémité d'entrée des pistons (14, 14a) pour réduire les pertes d'huile au minimum.

Abrégé anglais

A double-ended refrigerant compressor (30) consists of a pair of opposed
compressors (10a) each of which has a hollow piston (14, 14a) that is driven
by an armature (13, 13a) under the influence of electrical coils (12, 12a) to
compress refrigerant in the chambers (15, 15a). The armatures (13, 13a) have
oil slingers (31) to splash oil from the sump (17, 17a) to the pistons (14,
14a) and chambers (15, 15a). A cap (41) may be fitted over the inlet end of
the pistons (14, 14a) to minimise oil loss.

Revendications

6
CLAIMS
1. A single-ended linear refrigerant compressor comprising a body, an
electrical winding, an armature driven by the winding, a refrigerant chamber
or
barrel and a piston carried by the armature that is driven forward and
backward
in the barrel to compress refrigerant and wherein the body has an oil sump and
at least one oil slinger adapted to splash oil from the sump to the barrel and
piston.
2. A double-ended linear refrigerant compressor comprising a housing
defining a pair of opposed bodies each body having an electrical winding, an
armature driven by the winding, a refrigerant chamber or barrel and a piston
carried by the armature that is driven forward and backward in the barrel to
compress refrigerant therein and wherein the housing has an oil sump and at
least one oil slinger adapted to splash oil from the sump towards each barrel
and piston.
3. A refrigerant compressor according to claim 1 or claim 2 wherein the or
each oil slinger is mounted on the or each armature.
4. A refrigerant compressor according to claim 3 wherein there is a plurality
of oil slingers extending outwardly from the periphery of each armature.
5. A refrigerant compressor according to any one of the preceding claims
wherein the or each piston is hollow and has an inlet port for the refrigerant
and
further including a cap over the piston inlet, said cap having a plurality of
passageways around its periphery disposed at an angle to the line of
movement of the piston to allow refrigerant to enter the piston

7
6. A refrigerant compressor according to claim 5 wherein the cap is a press
fit over the inlet port of the hollow piston.
7. A refrigerant compressor according to claim 6 wherein the cap has an
end portion and a skirt portion surrounding the inlet port of the hollow
piston
and wherein the passageways are formed in the skirt portion.

Description

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SINGLE: AND DOUBLE-ENDED COMPRESSORS
FIELD OF THE INVENTION
This invention relates to linear refrigerant compressors and more
particularly to the oiling of such compressors including double-ended linear
compressors.
BACKGROUND ART
A linear refrigerant compressor consists of an armature with a piston
attached to it and a barrel where the refrigerant gas is compressed by the
piston. The armature moves backward and forward in a linear motion. The
energy associated with this movement is transferred to the body of the
compressor.
In a single-ended compressor only one armature is moving, and thus the
whole body of the compressor will be vibrating as well. This vibration creates
splashes of oil that help to lubricate the barrel and piston of the
compressor.
In a double-ended compressor the armatures are moving together with
the same amplitude, but in opposition directions. So that the total energy
transferred to the body is almost zero i.e. the compressor is not vibrating.
Although the lack of vibration makes the compressor quiet, it creates a
problem with the oiling as there is nothing to stir up the oil. This can lead
to
poor lubrication of the barrel and piston and to seizing of the compressor.
A similar problem will arise in respect of a single-ended compressor
made with a passive resonator which incorporates some other method of
eliminating vibration.
It is an object of this invention to overcome this problem by adding a
means to stir up the oil as the armature moves backward and forward.
SUMMARY OF THE INVENTION
According to one aspect of the invention there is provided a

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single-ended linear refrigerant compressor comprising a body, an electrical
winding, an armature driven by the winding, a refrigerant chamber or barrel
and
a piston carried by the armature that is driven forward and backward in the
barrel to compress refrigerant and wherein the body has an oil sump and at
least one oil stinger adapted to splash oil from the sump to the barrel and
piston.
According to another aspect of the invention there is provided a
double-ended linear refrigerant compressor comprising a housing defining a
pair of opposed bodies each having an electrical winding, an armature driven
by the winding, a refrigerant chamber or barrel and a piston carried by the
armature that is driven forward and backward in the barrel to compress
refrigerant therein and wherein the housing has an oil sump and at least one
oil
stinger adapted to splash oil from the sump towards each barrel and piston.
Preferably, the ar each oil stinger is mounted on the armature.
In a preferred embodiment of the invention, a plurality of oil stingers are
spaced evenly around the periphery of each armature.
The or each piston has an inlet port for the refrigerant and in order to
minimise oil loss, the piston inlet may be covered by a cap having a plurality
of
passageways around its periphery disposed at an angle to the line of
movement of the piston.
BRIEF DESCRIPTION OF THE DRAWINGS
Fig. 1 is a cross-sectional view of a single-ended refrigerant compressor
according to the prior art,
Fig. 2 is a cross-sectional view of a double-ended refrigerant
compressor according to the prior art,
Fig. 3 is a cross-sectional view of a double-ended refrigerant
compressor according to one embodiment of the invention,

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Fig. 4 is a view taken along lines A-A of Fig. 3,
Fig. 5 is a view similar to Fig. 3 of another embodiment of
the invention,
Fig. 6 is a view taken along lines B-B of Fig. 4,
Fig. 7 is an enlarged view of one piston of the double-ended
refrigerant compressor shown in Fig. 3 which has a
modified cap,
Fig. 8 is an enlarged front end view of the cap shown in
Fig. 7, and
Fig. 9 is an enlarged side view of the cap shown in Fig. 7.
MODES OF PERFORMING THE INVENTION
The prior art single-ended refrigerant compressor 10 shown in Fig. 1
includes a body 11 that has an electrical winding 12 that drives an armature
13
in a reciprocating manner. A piston 14 carried by the armature 13 is driven
backwards and forwards in the chamber or barrel 15 compressing refrigerant
gas during its forward stroke.
Within the body 11 there is a quantity of lubricating oil 16 which, when
the piston 14 is stationary, is located in the sump 17. When the compressor 10
is operating, the linear motion of the armature imparts vibration to the body
of
the compressor which in turn creates splashes of oil that lubricate the barrel
15
and the piston 14.
The double-ended compressor 20 shown in Fig. 2 consists of opposed
single-ended compressors 10, 10a which have a body 11, 11a, an electrical
winding 12, 12a, an armature 13, 13a, piston 14, 14a, barrel 15, 15a, sump 17,
17a and oil 16 and 16a. The armatures 13 and 13a are driven by the windings
12 and 12a with the same amplitude but in opposite direction with the end
result that the total energy transferred to the bodies 11 and 11 a is almost
zero

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and thus there is little, if any, vibration of the double-ended compressor 20
as a
whole.
This lack of vibration leads to poor lubrication of the pistons 14 and 14a
and barrels 15 and 15a as less oil is being splashed onto the pistons and
barrels.
The double-ended refrigerant compressor 30 shown in Figs. 3 and 4 is
substantially similar to that shown in Fig. 2 except that a plurality of oil
paddles
or stingers 31 are mounted around the periphery 32 of the armatures 13 and
13a. As can be seen in Fig. 4, the stingers 31 are long enough to pass through
the sump 17 and 17a to splash the oil around the bodies 11 and 11 a and onto
the pistons 14 and 14a and barrels 15 and 15a to lubricate them.
in this instance, there are 8 stingers 31 spaced evenly around the
periphery 32 of the armatures 13 and 13a to take account of any disposition of
the armatures 13 and 13a around the windings 12 and 12a during assembly
and operation of the compressor.
As shown in Fig. 4, this embodiment of the invention provides two
stingers 31 in the sump 17 and 17a at the one time but this need not be so. A
single stinger 31 can be used. The shape and configuration of the or each
stinger 31 is determined according to operational requirements for the
lubrications of the compressor.
The compressor shown in Figs. 5 and 6 is substantially similar to that
shown in Figs. 3 and 4 and thus the same numerals are used for the same
components. The embodiment of the invention shown in Figs 5 and 6 has
been devised to address a problem that can arise in relation to oil leaving
the
compressor. Refrigerant flow is in the direction of arrows R.
Part of the oil 16 stirred up by the stingers 31 can enter the inlet port 40
of the pistons 14 and 14a and then pumped via the inlet and outlet valves from

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the compressor into the system. This can lead to a situation where a large
part
of the oil is pumped out of the compressor resulting in poor lubrication of
the
piston and barrel.
To prevent or at least alleviate this problem, the inlet ports 40 are
5 provided with a cap 41 that has a plurality of passageways or gas inlet
ports 42
around its perimeter that are directed at angles of 90° to the line of
movement
of the pistons 14 and 14a. The purpose of the holes 42 is to allow the
refrigerant to enter the suction ports 40 but to prevent or at least hinder
the oil
16 entering the inlet ports 40. The holes are, in this instance, approximately
1
to 2mm in diameter.
The cap 50 shown in Figs. 7 to 9 , has an end portion 51 and a skirt
portion 52 which engages the end of the piston 14 with has inlet ports 53
spaced around the end of the skirt portion 52 allowing gas to enter the
suction
port 40. Ribs 54 around the interior of the skirt portion 52 between the inlet
ports 53 provide a press fit of the cap 50 onto the piston 14 when the cap 50
is
pressed up against the piston-supporting collar 55 carried by the armature 13.
Various other modifications may be made in details of design and
construction without departing from the scope and ambit of the invention. For
example, the or each oil stinger could be mounted on the spring that is
positioned between the armature and the barrel.

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