U.S. patent number 3,584,980 [Application Number 04/783,533] was granted by the patent office on 1971-06-15 for two-speed compressor.
This patent grant is currently assigned to Lennox Industries Inc.. Invention is credited to Richard E. Cawley, Charles B. Ellis.
United States Patent |
3,584,980 |
Cawley , et al. |
June 15, 1971 |
TWO-SPEED COMPRESSOR
Abstract
A refrigerant compressor having a two-speed compressor motor
therein for driving a compression mechanism selectively at a
relatively high speed and at a relatively low speed to effect
capacity control. For example, a two-winding four-pole motor would,
during two-pole operation, rotate at about 3,600 r.p.m., and during
four-pole operation at about 1,800 r.p.m. A two-stage pump is
provided for cooperating with the crankshaft to provide for
adequate lubrication of the crankshaft bearing surfaces during both
high-speed and low-speed operation of the compressor motor.
Inventors: |
Cawley; Richard E. (Hurst,
TX), Ellis; Charles B. (Fort Worth, TX) |
Assignee: |
Lennox Industries Inc.
(N/A)
|
Family
ID: |
25165815 |
Appl.
No.: |
04/783,533 |
Filed: |
December 13, 1968 |
Current U.S.
Class: |
417/372 |
Current CPC
Class: |
A01K
63/042 (20130101); H02K 7/085 (20130101); A01K
63/04 (20130101); F25B 31/02 (20130101) |
Current International
Class: |
A01K
63/04 (20060101); F25B 31/02 (20060101); F25B
31/00 (20060101); H02K 7/08 (20060101); F04b
039/02 () |
Field of
Search: |
;230/206,207,12 ;62/215
;318/224 ;417/372 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Walker; Robert M.
Claims
We claim:
1. In a refrigerant compressor including compression mechanism
within a sealed outer casing, said compression mechanism including
an upright crankshaft means having at least one longitudinally
extending pump passage therein offset from the rotational axis of
the crankshaft means for supplying lubricant to surfaces to be
lubricated, motor means within the outer casing for actuating the
compression mechanism, and a lubricant sump in the compressor, the
improvement characterized by said motor means comprising a
four-pole two-winding drive motor for driving the compression
mechanism at a first high speed and a second lower speed to control
capacity of the compressor, two-pole operation providing said high
speed and four-pole operation providing said lower speed, and a
two-stage pump mechanism operatively driven by the drive motor for
assuring adequate lubrication whether the drive motor is operating
at said high speed or said lower speed, said pump mechanism
including means defining first inlet opening means offset from the
rotational axis of the crankshaft means for ingesting lubricant
from the sump, a first-stage pressurizing opening transversely
disposed in said crankshaft means, said first-stage pressurizing
opening communicating with said first inlet opening means, a
second-stage pressurizing opening transversely disposed in said
crankshaft means, passage means communicating with said first-stage
pressurizing opening with said second-stage pressurizing opening,
said second-stage pressurizing opening also communicating with said
pump passage, the two-stage pump mechanism assuring adequate
lubrication of said surfaces to be lubricated at said lower speed
operation of said drive motor.
2. A refrigerant compressor as in claim 1 wherein the means
defining first inlet opening means comprises a thrust washer fixed
in said compression mechanism below the crankshaft means and having
at least one axially offset inlet opening therein, said thrust
plate having a transversely disposed bore separate from said inlet
opening, said transversely disposed bore defining a portion of said
passage means.
3. A refrigerant compressor as in claim 2 wherein the crankshaft
means includes crankshaft and a pump impeller connected thereto,
said first-stage pressurizing opening being in said pump
impeller.
4. A refrigerant compressor as in claim 3 wherein said passage
means includes an axial bore in said crankshaft which communicates
at one end with an axial bore in said thrust washer that in turn
communicates with the tranversely disposed bore in the thrust
washer, whereby lubricant ingested through said inlet opening
passes through the first-stage pressurizing opening, passage means,
and second-stage pressurizing opening to the pump passage.
5. A refrigerant compressor as in claim 3 wherein the passage means
includes an annular chamber defined between the thrust washer, pump
impeller and compression mechanism, said annular chamber
communicating with said first-stage pressurizing opening and said
transversely disposed bore in said thrust washer.
6. A refrigerant compressor as in claim 5 wherein the thrust washer
has a continuous annular groove in the top surface thereof
communicating with the inlet opening means, the top surface of the
thrust washer abutting the bottom surface of the pump impeller,
said annular groove providing continuous feed of lubricant from the
inlet opening means to said first-stage pressurizing opening in the
pump impeller.
Description
BACKGROUND OF THE INVENTION
This invention relates to a hermetic refrigerant compressor
utilizing a motor operable at different predetermined increments
for driving the compression mechanism so as to effect capacity
control. In another aspect, this invention relates to a hermetic
refrigerant compressor having a motor operable at different fixed
increments, for example, full-speed and half-speed, with a
two-stage pump associated with the crankshaft for assuring adequate
lubrication at both speeds of operation.
Refrigerant compressors have generally been designed to operate at
a relatively constant speed. In use, the load on the refrigeration
system in which the compressor is utilized may vary, resulting in
several off-on cycles as well as inefficient operation of the
compressor unless the capacity of the compressor can be varied to
comply with system variation. One method of effecting capacity
control has been to bypass discharge gases from the discharge line
directly to the suction line or suction side of the refrigeration
system--a highly inefficient method. Still another arrangement
requires the use of capacity control valving and solenoids within
or in association with the compressor in order to vent the
discharge of cylinders to the suction manifold. This method is more
efficient than the discharge gas bypass arrangement, but still less
efficient than desired.
An object of the present invention is to provide an improved
refrigerant compressor employing a compressor motor operable at
different fixed increments of speed for effecting capacity
control.
Another object of this invention is to provide an improved hermetic
compressor having a drive motor operable at different fixed
increments of speed, such compressor including multistage pump
means to assure adequate lubrication of the crankshaft bearing
surfaces during all operating speeds. Other objects and advantages
of the present invention will become more apparent hereinafter.
BRIEF DESCRIPTION OF THE DRAWING
The attached drawing illustrates a preferred embodiment of the
invention in which like numerals refer to like elements and in
which:
FIG. 1 is a side elevational view, partially in section and with
parts broken away, of a hermetic refrigerant compressor embodying
the present invention;
FIG. 2 is an enlarged cross-sectional view of the two-stage pump
mechanism of the present invention;
FIG. 3 is a bottom view of the two-stage pump mechanism of FIG. 2;
and
FIG. 4 is a cross-sectional view of the pump impeller.
DETAILED DESCRIPTION OF THE INVENTION
Referring to FIG. 1, there is illustrated a compressor embodying
the present invention. The compressor 10 comprises a gastight,
hermetically enclosed outer casing or housing including an upper
shell 12 and a lower shell 14 integrally joined to one another, as,
for example, by welding. To the bottom of the exterior surface of
the lower shell 14 are welded a plurality of legs 16 by means of
which legs the compressor may be supported in an upright position
within a condensing unit or an air-conditioning unit.
Supported within the outer casing of the compressor 10 is a
compression mechanism 18 which includes a compressor block having a
crankcase portion 20 and a motor flange portion 22. An annular
sleeve 24 made from sheet metal surrounds the crankcase portion 20
of the compressor block and cooperates therewith to define an
annular discharge gas cavity 23 in the compression mechanism. A
heat shield 26 is disposed about the annular sleeve in spaced
relationship thereto.
The annular sleeve 24 includes an out-turned upper flange 28.
Secured to the lower shell 14 of the outer casing is an annular
flange member 29. Spring means 32 cooperate between the flange 28
and flange member 29 for resiliently supporting the compression
mechanism 18 within the outer casing of compressor 10.
Provided within the compressor block are a plurality of radially
oriented cylinders 30. Though a four-cylinder compressor is
illustrated, it will be understood that the present invention may
be used in a hermetic refrigerant compressor having other cylinder
configurations. Cylinder sleeve or liners 33 are provided in each
of the cylinders 30 and a piston 34 is slidably mounted for
reciprocation within each of the cylinder liners 33. Each piston 34
has mounted therein a wrist pin 36 upon which is journaled one end
of a connecting rod 38. The other end of each connecting rod 38 is
affixed to the eccentric portion 40 of drive shaft or crankshaft
42.
Provided at the end of each cylinder 30 for closing the end of each
cylinder cavity is a valve assembly 60. The valve assemblies 60
each comprise a discharge valve unit and a suction valve unit
operable in a known manner. Each valve assembly 60 is held in place
in the end of a cylinder 30 by a cylinder head or cap 62. A
Belleville spring 64 and a retaining ring 66 cooperate with the
cylinder head 62 to maintain the head in position closing the end
of the cylinder. The annular space 23 provided within the
compression mechanism between the compressor block and the sleeve
24 communicates each of the cylinders and receives the discharge
gases from the cylinders and conveys them to the discharge line
72.
The drive shaft 42 is disposed in an upright position within the
compression mechanism 18 and is connected at its upper end to the
rotor 44 of the electric drive motor 46. The motor includes a
stator 48 which is supported within the motor flange portion 22 of
the compressor block and the rotor 44 which is inductively
connected to the stator 48.
Enclosing the top of the motor 46 is an end cap 50 which is
suitably connected to top of the motor flange portion 22 of the
compressor block.
Drive shaft 42 is journaled at its lower end within a lower bearing
52 mounted in lower bearing head 54. The lower bearing head 54 is
maintained in position by a suitable wedge-lock spring or retaining
ring 56 seated within an annular groove in the lower crankcase
portion 20 of the compressor block. Intermediate its ends the drive
shaft 42 is journaled within the spaced bearings 57 and 58 in the
hub portion or partition portion 21 of the compressor block.
Suction gas enters the outer casing or housing of the compressor
via the suction line inlet 74 and flows into a first compartment
defined between the outer casing and the compression mechanism
below the flange 29. The gas passes from the first compartment into
a second compartment or annular space defined between the flanges
29 and 28 and then into a third compartment defined between the
outer casing and the top of the compression mechanism 18. From the
third compartment, the suction gas passes through the opening 51 in
the top of the end cap 50 over the electric motor 46 for cooling
same and then through the openings 76 in the compressor block into
the cylinders 30. The gases are compressed within the cylinders and
forced through the valve assemblies 60 into the annular discharge
gas cavity 23. From the annular discharge gas cavity 23, the
compressed gas passes through the discharge line 72 to the
condenser of the refrigeration system in which the compressor is
utilized.
A plurality of terminals 78 are provided in the top of the upper
shell 12 in order to conduct electric current from a suitable
source to the electric motor 46 and to provide for connection of
suitable motor protection while preserving the hermetic nature of
the compressor.
In larger size refrigerant compressor, for example, on the order of
10-ton capacity and four cylinders, it is sometimes difficult to
employ mechanical unloaders because of balance and control
problems. A unique solution to the problem of capacity control in
such compressors is to provide a multipole electric motor operable
at different fixed increments of speed by which the capacity of the
refrigeration system can be varied. For example, a four-pole
two-winding electric motor can be utilized to provide full capacity
during two-pole operation and one-half capacity during four-pole
operation. The characteristics of one form of motor embodying the
present invention would be as follows: ##SPC1## ##SPC2##
It is seen that in such motor the minimum speed during high-speed
or two-pole operation would be on the order of 3,235--3,510 r.p.m.
At half-speed or four-pole operation the motor speed would be on
the order of 1,620--1,750 r.p.m.
It has been found that by taking advantage of total refrigeration
system characteristics and reducing the maximum load requirement
during low-speed operation, minimum required efficiencies of not
less than about 80 percent can be maintained during both high-speed
and low-speed operation with a less expensive motor design than,
say, a constant torque two-speed motor.
In use, the known pump means of the prior compressors would
function satisfactorily in the novel compressors of this invention
during high-speed operation, but provided inadequate lubrication
during low-speed operation. The hermetic compressor 10 of the
present invention has been provided with unique two-stage pump
means 80 for assuring adequate lubrication of the crankshaft
bearing surfaces during both high-speed and low-speed operation.
The upright drive shaft or crankshaft 42 is provided with a
longitudinally disposed pump passage 81 which has at its upper end
radially disposed passages 82 and 84 for lubricating the bearing
surfaces between the crankshaft 42 and bearings 57 and 58. The
passages 83 and 85 communicate with the upper end of the pump
passage 81 to vent refrigerant from the pump passage at startup of
the compressor. Lubricant is supplied to the lower bearing 52
through the radially disposed passage 86.
Disposed in an opening in the bottom of the lower bearing head 54
and fixedly secured thereto is a thrust plate 90. Openings 91 in
the thrust plate 90 provide inlet opening means for communicating
the rotating elements of two-stage pump 80 with lubricant in the
sump defined between the compression mechanism and the lower shell
14. Lubricant passes from the openings 91 through an inlet opening
92 in the pump impeller 93 into radially disposed or transversely
disposed passage 94 in the pump impeller 93. The passage 94
provides for the first-stage pressurization of the ingested
lubricant. Lubricant is discharged from passage 94 into the annular
space 96 between the rotating pump impeller 93 and the inner wall
of the lower bearing head 54. The impeller 93 is connected to the
drive shaft 42 by suitable fastening means, for example, machine
screws 98. The lubricant passes from the annular space 96 through a
transverse passage 100 in the fixed thrust plate 90 and then
upwardly through a central passage 102 in the pump impeller 93 into
a recess 103 in the bottom of the drive shaft. From recess 103, the
lubricant passes into the radially disposed passage 86 and then
into the pump passage 81 for transfer to the crankshaft bearing
surfaces. A second-stage pressurizing of the lubricant is effected
in the passage 86.
In operation it has been found that the lubricant will be supplied
to the radially disposed outlets 86, 84 and 82 during both
high-speed and low-speed operation of the compressor under desired
pressure. The use of a conventional single-stage pump was found
inadequate to supply desired lubricant pressure during low-speed
operation. Screen 110 is affixed to the lower bearing head to
prevent impurities in the sump from entering the two-stage pump
80.
Referring to FIGS. 2, 3 and 4 there is better illustrated the
details of the two-stage pump of the present invention. The thrust
plate 90 has four openings 91 therein which serve as inlet openings
for communicating the two-stage pump with the oil in the sump. A
continuous annular groove 112 is provided in the top of the thrust
plate 90 for providing continuous feed of lubricant to the pump
impeller 93. Provided in the thrust plate 90 in a plane generally
transverse or at right angles to the axes of the four openings 91
is a bore 100. The pump impeller 93 of the two-stage pump 80 rests
upon the thrust plate 90 during normal operation. The pump impeller
93 is fixed to the drive shaft or crankshaft 42 for rotation
therewith by means of the fastening means 98. Lubricant will be
ingested through the passages 91 in the thrust plate 90, into the
annular groove 112 in the top of the thrust plate, through the
inlet opening 92 in the pump impeller 93 into the radially disposed
passage 94 of the pump impeller 93 where the first-stage
pressurization occurs. The lubricant will then pass from the
radially disposed passage 94 through passage means defined in part
by annular chamber 96 between the impeller 93, washer or thrust
plate 90 and lower bearing head 54, the bore 100 in the thrust
plate 90 and the axially aligned upright bore 102 in the impeller
93 for passage through the second-stage pressurized passage 86 into
the upright axially offset passage 81. The two-stage pump of the
present invention functions effectively during both high-speed and
low-speed operation of the compressor motor to provide adequate
lubricant pressurization during all modes of operation. A minimum
number of components are required to be added to the compressor
mechanism while maintaining the desired lubrication.
There has been provided by the present invention a hermetic
compressor utilizing a motor for driving the compression mechanism
within the compressor selectively at different fixed increments of
speed so as to provide for capacity control without auxiliary
components such as capacity control valving and solenoids. In one
presently preferred form, the motor is a two-winding four-pole
motor, with two-pole operation providing the higher speed (about
3600 r.p.m.) and four-pole operation providing the lower speed
(about 1,800 (r.p.m.). The hermetic compressor is further provided
with a novel two-stage pump means which will maintain desired
pressurized lubrication during both high-speed and low-speed
operation of the compressor motor.
While there has been shown and described a presently preferred
embodiment of the invention, it will be obvious that other
embodiments will be apparent to those skilled in the art. It is,
therefore, intended that the invention be limited only within the
scope of the appended claims.
* * * * *