Title of Invention

SCROLL MACHINE

Abstract A compressor (10) includes a normally open discharge valve assembly (130) for controlling compressed refrigerant flow from the discharge chamber (80) through the compression members (56, 70). This controlling of flow results in an increased performance for the compressor (10) by reducing recompression volume and the elimination of reverse rotation at shut down. The discharge valve assembly (130) includes a valve seat (132), a valve plate (134) and a valve stop (136) secured within a recess (78) formed within the compressor (10) with a wave ring retainer (138). The valve stop (136) and the valve seat (132) include a contoured surface that is engaged by the valve plate (134) when it opens and closes. The contoured surface controls the movement of the valve plate (134).
Full Text SCROLL MACHINE
FIELD OF THE INVENTION
[0001] The present invention relates to a scroll machine. More particularly, the present
invention relates to a scroll compressor with a unique retention system for a direct discharge valve
system.
BACKGROUND AND SUMMARY OF THE INVENTION
[0002] Scroll machines are becoming more and more popular for use as compressors in both
refrigeration as well as air conditioning and heat pump applications due primarily to their capability for
extremely efficient operation. Generally, these machines incorporate a pair of intermeshed spiral
wraps, one of which is caused to orbit relative to the other so as to define one or more moving
chambers that progressively decrease in size as they travel from an outer suction port towards a
center discharge port. An electric motor is normally provided that operates to drive the orbiting scroll
member via a suitable drive shaft.
[0003] Because scroll compressors depend upon successive chambers for suction,
compression, and discharge processes, suction and discharge valves in general are not required.
However, the performance of the compressor can be increased with the incorporation of a
discharge valve. One of the factors that will determine the level of increased performance is
the reduction of what is called recompression volume. The recompression volume is the volume
of the discharge chamber and the discharge port of the compressor when the discharge


chamber is at its smallest volume. The minimization of this recompression
volume will result in a maximizing of the performance of the compressor. In
addition, when such compressors are shut down, either intentionally as a result
of the demand being satisfied, or unintentionally as a result of a power
interruption, there is a strong tendency for the backflow of compressed gas from
the discharge chamber and to a lesser degree for the gas in the pressurized
chambers to effect a reverse orbital movement of the orbiting scroll member and
its associated drive shaft. This reverse movement often generates noise or
rumble, which may be considered objectionable and undesirable. Further, in
machines employing a single phase drive motor, it is possible for the compressor
to begin running in the reverse direction should a momentary power interruption
be experienced. This reverse operation may result in overheating of the
compressor and/or other inconveniences to the utilization of the system.
Additionally, in some situations, such as a blocked condenser fan, it is possible
for the discharge pressure to increase sufficiently to stall the drive motor and
effect a reverse rotation thereof. As the orbiting scroll orbits in the reverse
direction, the discharge pressure will decrease to a point where the motor again
is able to overcome this pressure head and orbit the scroll member in the forward
direction. However, the discharge pressure will again increase to a point where
the drive motor is stalled and the cycle is repeated. Such cycling is undesirable
in that it is self-perpetuating. The incorporation of a discharge valve can reduce
or eliminate these reverse rotation problems.


[0004] A primary object of the present invention resides in the provision
of a very simple and unique retention system for a discharge valve, which is
associated with the non-orbiting scroll and which can easily be assembled into a
conventional gas compressor of the scroll type without significant modification of
the overall compressor design. The discharge valve operates to minimize the
recompression volume and at compressor shut down operates to prohibit
backflow of the discharge gas through the compressor and thus driving the
compressor in the reverse direction. Prohibiting the reverse operation of the
compressor eliminates the normal shut down noise and other problems
associated with such reverse rotation. The retention system includes a wave ring
retainer that is disposed within a groove in the non-orbiting scroll member. This
groove is located adjacent the discharge valve. The wave ring retainer biases
the discharge valve against the non-orbiting scroll member, but the wave ring
retainer will deflect at a specified pressure to increase the flow area for the
discharge gas.
[0005] These and other features of the present invention will become
apparent from the following description and the appended claims, taken in
conjunction with the accompanying drawings.
[0006] Further areas of applicability of the present invention will
become apparent from the detailed description provided hereinafter. It should be
understood that the detailed description and specific examples, while indicating
the preferred embodiment of the invention, are intended for purposes of
illustration only and are not intended to limit the scope of the invention.


BRIEF DESCRIPTION OF THE DRAWINGS
[0007] The present invention will become more fully understood from
the detailed description and the accompanying drawings, wherein:
[0008] Figure 1 is a vertical sectional view through the center of a scroll
compressor that incorporates a retention system for a discharge valve assembly
in accordance with the present invention;
[0009] Figure 2 is a top elevational view of the compressor shown in
Figure 1 with the cap and a portion of the partition removed;
[0010] Figure 3 is an enlarged view of the floating seal assembly and
discharge valve assembly illustrated in Figure 1;
[0011] Figure 4A is an enlarged view of the discharge valve assembly
illustrated in Figures 1 and 3 with the discharge valve being biased against the
non-orbiting scroll member;
[0012] Figure 4B is an enlarged view of the discharge valve assembly
illustrated in Figures 1 and 3 with the discharge valve being spaced from the
non-orbiting scroll member; and
[0013] Figure 5 is an exploded perspective view of the retention system
of the discharge valve assembly shown in Figures 1 and 3.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
[0014] The following description of the preferred embodiment(s) is
merely exemplary in nature and is in no way intended to limit the invention, its
application, or uses:


[0015] Referring now to the drawings in which like reference numerals
designate like or corresponding parts throughout the several views, there is
shown in Figure 1 a scroll compressor that incorporates a retention system for a
discharge valving system in accordance with the present invention and which is
designated generally by reference numeral 10. Compressor 10 comprises a
generally cylindrical hermetic shell 12 having welded at the upper end thereof a
cap 14 and at the lower end thereof a base 16 having a plurality of mounting feet
(not shown) integrally formed therewith. Cap 14 is provided with a refrigerant
discharge fitting 18. Other major elements affixed to the shell include a
transversely extending partition 22 that is welded about its periphery at the same
point that cap 14 is welded to shell 12, a lower bearing housing 24 that is suitably
secured to shell 12 and a two piece upper bearing housing 26 suitably secured to
lower bearing housing 24.
[0016] A drive shaft or crankshaft 28 having an eccentric crank pin 30
at the upper end thereof is rotatably joumaled in a bearing 32 in lower bearing
housing 24 and a second bearing 34 in upper bearing housing 26. Crankshaft 28
has at the lower end a relatively large diameter concentric bore 36 that
communicates with a radially outwardly inclined smaller diameter bore 38
extending upwardly therefrom to the top of crankshaft 28. The lower portion of
the interior shell 12 defines an oil sump 40 that is filled with lubricating oil to a
level slightly above the lower end of a rotor 42, and bore 36 acts as a pump to
pump lubricating fluid up crankshaft 28 and into bore 38 and ultimately to all of
the various portions of the compressor that require lubrication.


[0017] Crankshaft 28 is rotatively driven by an electric motor including
a stator 46, windings 48 passing therethrough and rotor 42 press fitted on
crankshaft 28 and having upper and lower counterweights 50 and 52,
respectively.
[0018] The upper surface of upper bearing housing 26 is provided with
a flat thrust bearing surface 54 on which is disposed an orbiting scroll member 56
having the usual spiral vane or wrap 58 extending upward from an end plate 60.
Projecting downwardly from the lower surface of end plate 60 of orbiting scroll
member 56 is a cylindrical hub having a journal bearing 62 therein and in which
is rotatively disposed a drive bushing 64 having an inner bore 66 in which crank
pin 30 is drivingly disposed. Crank pin 30 has a flat on one surface that drivingly
engages a flat surface (not shown) formed in a portion of bore 66 to provide a
radially compliant driving arrangement, such as shown in Assignee's U.S. Letters
Patent 4,877,382, the disclosure of which is hereby incorporated herein by
reference. An Oldham coupling 68 is also provided positioned between orbiting
scroll member 56 and bearing housing 24 and keyed to orbiting scroll member 56
and a non-orbiting scroll member 70 to prevent rotational movement of orbiting
scroll member 56. Oldham coupling 68 is preferably of the type disclosed in
Assignee's co-pending U.S. Letters Patent 5,320,506, the disclosure of which is
hereby incorporated herein by reference.
[0019] Non-orbiting scroll member 70 is also provided having a wrap
72 extending downwardly from an end plate 74 that is positioned in meshing
engagement with wrap 58 of orbiting scroll member 56. Non-orbiting scroll


member 70 has a centrally disposed discharge passage 76 that communicates
with an upwardly open recess 78 which, in tum, is in fluid communication with a
discharge muffler chamber 80 defined by cap 14 and partition 22. An annular
recess 82 is also formed in non-orbiting scroll member 70 within which is
disposed a floating seal assembly 84. Recesses 78 and 82 and seal assembly
84 cooperate to define axial pressure biasing chambers, which receive
pressurized fluid being compressed by wraps 58 and 72 so as to exert an axial
biasing force on non-orbiting scroll member 70 to thereby urge the tips of
respective wraps 58, 72 into sealing engagement with the opposed end plate
surfaces of end plates 74 and 60, respectively. Seal assembly 84 is preferably of
the type described in greater detail in U.S. Patent No. 5,156,539, the disclosure
of which is hereby incorporated herein by reference. Non-orbiting scroll member
70 is designed to be mounted to upper bearing housing 26 in a suitable manner
such as disclosed in the aforementioned U.S. Patent No. 4,877,382 or U.S.
Patent No. 5,102,316, the disclosure of which is hereby incorporated herein by
reference.
[0020] Referring now to Figures 2 and 3, floating seal assembly 84 is of
a coaxial sandwiched construction and comprises an annular base plate 102
having a plurality of equally spaced upstanding integral projections 104 each
having an enlarged base portion 106. Disposed on plate 102 is an annular
gasket assembly 108 having a plurality of equally spaced holes that mate with
and receive base portions 106. On top of gasket assembly 108 is disposed an
annular spacer plate 110 having a plurality of equally spaces holes that also


mate with and receive base portions 106. On top of plate 110 is an annular
gasket assembly 112 having a plurality of equally spaced holes that mate with
and receive projections 104. The assembly of seal assembly 84 is maintained by
an annular upper seal plate 114, which has a plurality of equally spaced holes
mating with and receiving projections 104. Seal plate 114 includes a plurality of
annular projections 116, which mate with and extend into the plurality of holes in
annular gasket assembly 112 and spacer plate 110 to provide stability to seal
assembly 84. Seal plate 114 also includes an annular upwardly projecting planar
sealing lip 118. Seal assembly 84 is secured together by swaging the ends of
projections 104 as indicated at 120.
[0021] Referring now to Figure 3, seal assembly 84 therefore provides
three distinct seals: first, an inside diameter seal at two interfaces 122; second,
an outside diameter seal at two interfaces 124; and, third, a top seal at 126.
Seals 122 isolate fluid under intermediate pressure in the bottom of recess 82
from fluid under discharge pressure in recess 78. Seals 124 isolate fluid under
intermediate pressure in the bottom of recess 82 from fluid under suction
pressure within shell 12. Seal 126 is between sealing lip 118 and an annular
seat portion on partition 22. Seal 126 isolates fluid at suction pressure from fluid
at discharge pressure across the top of seal assembly 84.
[0022] The diameter and width of seal 126 are chosen so that the unit
pressure between sealing lip 118 and the seat portion on partition 22 is greater
than normally encountered discharge pressure, thus ensuring consistent sealing
under normal operating conditions of compressor 10, i.e., at normal operating


pressure ratios. Therefore, when undesirable pressure conditions are
encountered, seal assembly 84 will be forced downward breaking seal 126,
thereby permitting fluid flow from the discharge pressure zone of compressor 10
to the suction pressure zone of compressor 10. If this flow is great enough, the
resultant loss of flow of motor-cooling suction gas (aggravated by the excessive
temperature of the leaking discharge gas) will cause a motor protector to trip
thereby the de-energizing motor. The width of seal 126 is chose so that the unit
pressure between sealing lip 118 and the seat portion of partition 22 is greater
than normally encountered discharge pressure, thus ensuring consistent sealing.
[0023] The scroll compressor as thus far broadly described is either
now known in the art or is the subject of other pending applications for patent or
patents of Applicant's Assignee.
[0024] The present invention is directed towards a retention system for
a normally open mechanical valve assembly 130, which is disposed within recess
78, which is formed in non-orbiting scroll member 70. While the present
invention is being described in conjunction with normally open mechanical valve
assembly 130, the retention system of the present invention can be used with
any other type of discharge valve also. Valve assembly 130 moves between a
first or closed condition, a second or open condition, and a third or fully open
condition during steady state operation of compressor 10. Valve assembly 130
will close during the shut down of compressor 10. When valve assembly 130 is
fully closed, the recompression volume is minimized and the reverse flow of
discharge gas through scroll members 56 and 70 is prohibited. Valve assembly


130 is normally open as shown in Figures 3 and 4A. The normally open
configuration for valve assembly 130 eliminates the force required to open valve
assembly 130 as well as eliminating any mechanical device needed to close
valve assembly 130. Valve assembly 130 relies on gas pressure differential for
closing.
[0025] Referring now to Figures 3-5, discharge valve assembly 130 is
disposed within recess 78 and it comprises a valve seat 132, a valve plate 134, a
valve stop 136 and a wave ring retainer 138. Valve seat 132 is a flat metal disc
shaped member defining a discharge passage 140, a pair of alignment apertures
142 and a cavity 144. Non-orbiting scroll member 70 defines a pair of alignment
bores. When apertures 142 are in registry with the alignment bores, discharge
passage 140 is aligned with discharge passage 76. The shape of discharge
passage 140 is the same as discharge passage 76. The thickness of valve seat
132, particularly in the area of cavity 144 is minimized to minimize the
recompression volume for compressor 10, which increases the performance of
compressor 10. The bottom surface of cavity 144 adjacent to valve plate 134
includes a contoured surface 148. The flat horizontal upper surface of valve seat
132 is used to secure valve plate 134 around its entire circumference.
Contoured surface 148 of cavity 144 provides for the normally open characteristic
of valve assembly 130. Contoured surface 148 may be a generally planar
surface a shown in Figure 4A or contoured surface 148 may be a curved surface.
While cavity 144 and contoured surface 148 are shown as a pocket within valve
seat 132, it is within the scope of the present invention to have cavity 144 and


thus surface 148 extend through the edge of valve seat 132. Also, it is within the
scope of the present invention to eliminate valve seat 132 and incorporate cavity
144 and surface 148 directly into and onto non-orbiting scroll 70 if desired.
[0026] Valve plate 134 is a flat thin metal disc shaped member that
includes an annular ring 150, a generally rectangular portion 152 extending
radially inward from ring 150 and a generally circular portion 154 attached to the
radial inner end of rectangular portion 152. Rectangular portion 152 is designed
to be smaller in width than circular portion 154. This reduced section therefore
has a lower bending load than circular portion 154, which results in a faster
opening of valve assembly 130. This reduced section of rectangular portion 152
is acceptable from a durability standpoint since contoured surface 148 reduces
the stress loading on this reduced section. The size and shape of portion 154 is
designed to completely cover discharge passage 140 of valve seat 132. The
generally circular shape of portion 154 eliminates valve breakage that is
associated with rectangular valve plates. In general, valve plates can have a
tendency to twist during the closing of the valve due to the pressure fluctuations
across the valve. When a rectangular shape valve twists before closing, the
outside corner of the rectangle will hit first causing high loading and the breakage
of the corner. The present invention, by using a generally circular portion to
close the valve, eliminates the possibility of this comer breakage. Valve plate
134 also includes a pair of bosses 156, which define a pair of alignment
apertures 158. When apertures 158 are in registry with apertures 142 of valve
seat 132, rectangular portion 152 positions circular portion 154 in alignment with


discharge passage 140. The thickness of valve plate 134 is determined by the
stresses developed in rectangular portion 152 as valve plate 134 deflects from its
closed position to its open position as described below.
[0027] Valve stop 136 is a thick metal, disc shaped member that
provides support and backing for valve plate 134 and valve seat 132. Valve stop
136 is similar in configuration to valve plate 134 and includes an annular ring
160, a generally rectangular portion 162 extending radially inward from ring 160,
a generally circular portion 164 attached to the radially inner end of rectangular
portion 162 and a support section 166 extending between circular portion 164
and ring 160 on the side of portion 164 opposite to portion 162. Valve stop 136
also includes a pair of bosses 168, which define a pair of alignment apertures
170. When apertures 170 are in registry with apertures 158 in valve plate 134,
rectangular portion 162 is aligned with rectangular portion 152 of valve plate 134
and it positions circular portion 164 in alignment with circular portion 154 of valve
plate 134. Rectangular portion 162 and circular portion 164 cooperate to define
a curved contoured surface 172.
[0028] Discharge valve assembly 130 is assembled to non-orbiting
scroll member 70 by first placing valve seat 132 within recess 78 with contoured
surface 148 facing upward while aligning apertures 142 with bores 146, which
aligns passage 140 with passage 76. Next, valve plate 134 is placed on top of
valve seat 132 within recess 78 while aligning apertures 158 with apertures 142,
which aligns circular portion 154 with passage 140. Next, valve stop 136 is
placed on top of valve plate 134 within recess 78 while aligning apertures 170


within apertures 158, which aligns portions 162 and 164 with portions 152 and
154, respectively. A roll pin 176 is inserted through each aligned set of apertures
170, 158 and 142 and press fit into each bore 146 to maintain the alignment of
these components. Finally, retainer 138 is installed within recess 78 to maintain
the assembly of valve assembly 130 with non-orbiting scroll member 70. The
assembly of retainer 138 sandwiches the entire annular ring 150 of valve seat
132 between the upper flat surface of valve seat 132 and ring 160 of valve stop
136 to secure and retain valve plate 134.
[0029] Retainer 138 is a wave ring retainer that is disposed within a
groove 180 formed into recess 78 of non-orbiting scroll member 70. The wave
shape of retainer 138 causes it to engage both the upper surface 182 and the
lower surface 184 of groove 180 to adequately retain discharge valve assembly
within recess 78, as shown in Figure 4A. The wave shape of retainer 138 also
allows for axial movement of discharge valve assembly due to the resilience and,
thus, compression of the wave ring retainer as shown in Figure 4B.
[0030] Discharge valve assembly 130 is normally in a condition
wherein valve plate 134 abuts the upper flat surface on valve seat 132.
Contoured surface 148 spaces valve plate 134 from valve seat 132 to provide for
the normally open characteristic of valve assembly 130. This allows limited fluid
flow from discharge muffler chamber 80 into the compression pockets formed by
scroll members 56 and 70. In order to close valve assembly 130, fluid pressure
within muffler chamber 80 biases valve plate 134 against contoured surface 148
of valve seat 132 when the fluid pressure in chamber 80 is greater than the fluid


pressure within the central most fluid pocket formed by scroll members 56 and
70. During operation of compressor 10, the fluid pressure differential between
fluid in discharge chamber 80 and fluid within the central most fluid pocket
formed by scroll members 56 and 70 will move valve plate 134 between
abutment with contoured surface 148 of valve seat 132 and abutment with valve
stop 136 or between a first closed position and a second open position. The
normally open position of valve assembly 130 eliminates the force that is
required to open a typical discharge valve. The elimination of this force lowers
the pressure differential for operating the valve, which, in turn, lowers power
losses. In addition the normally open feature reduces the sound generated
during the closing of the valve due to the gradual closing of the valve rather than
the sudden closure of a normally closed valve. Contoured surface 148 provides
for this gradual closing feature. The valve of the present invention operates
solely on pressure differentials. Finally, the unique design for valve assembly
130 provides a large flow area to improve the flow characteristics of the system.
[0031] When valve plate 134 is in its second or open position,
additional discharge pressure within discharge passage will react against
discharge valve assembly 130 and it will eventually exceed the spring force being
applied by wave ring retainer 138. Discharge valve assembly 130 will then move
axially upward to the position shown in Figure 4B, the third or fully open position,
to allow fluid flow around the outer periphery of discharge valve assembly 130.
[0032] Valve plate 134 is sandwiched between valve seat 132 and
valve stop 136 with annular ring 160 of valve stop 136 abutting annular ring 150


of valve plate 134, which, in turn, abuts the upper flat surface of valve seat 132.
Rectangular portion 152 and circular portion 154 normally lie in an unstressed
condition in a generally horizontal position as shown in Figure 4A. The deflection
of valve plate 134 occurs in rectangular portion 152 .and circular portion 154. To
fully close, portions 152 and 154 deflect toward valve seat 132 and to open
portions 152 and 154 deflect in the opposite direction toward valve stop 136.
The stresses encountered by valve plate 134 are stresses that are both plus and
minus in direction from the neutral normally open position. Thus, when
comparing the stresses of valve plate 134 with those encountered by the flap
valve of a normally closed discharge valve, the stresses are significantly
reduced. The normally closed flap valve begins in a position adjacent a valve
seat when the flap valve is unstressed. As the valve begins to open the stresses
begin at the unstressed condition and continue to grow as the flap valve opens.
Thus they are undirectional from the unstressed condition. The present
invention, by centering the stressed conditions of valve plate 134 on both sides of
the unstressed condition significantly reduces the stress loading experienced by
valve plate 134.
[0033] In order to further reduce the stress loading and thus the life of
valve plate 134, the shape of contoured surface 148 of valve seat 132 and
contoured surface 172 of valve stop 136 are chosen to ensure a gradual loading
and minimizing of the stresses by distributing the loads over a broader area.
Finally, the rounded contours and transitions between ring 150, rectangular
portion 152 and circular portion 154 are designed to eliminate stress risers. This


elimination of stress risers, the equal distribution of the load and the reduction in
the maximum stresses encountered significantly improves the life and
performance for discharge valve assembly 130.
[0034] While the above detailed description describes the preferred
embodiment of the present invention, it should be understood that the present
invention is susceptible to modification, variation and alteration without deviating
from the scope and fair meaning of the subjoined claims.

WE CLAIM
1. A scroll machine (10) comprising:
- a first scroll member (70) having a first spiral wrap (72) projecting outwardly
from a first end plate (74);
- a second scroll member (56) having a second spiral wrap (58) projecting
outwardly from a second end plate (60), said second spiral wrap (58) being
intermeshed with said first spiral wrap (72);
- a discharge chamber (80);
- a drive member (28) for causing said scroll members (70, 56) to orbit relative to
one another whereby said spiral wraps (72, 58) will create pockets of
progressively changing volume between a suction pressure zone and a discharge
pressure zone, said discharge pressure zone being in communication with said
discharge chamber (80); and
- a discharge valve (130) disposed between said discharge pressure zone and said
discharge chamber (80), said discharge valve (130) being disposed within a
recess (78) formed by said first scroll member (70), said discharge valve (130)
being operable in first, and second positions, wherein:

- said first position is a closed position where fluid flow between said discharge
chamber (80) and said discharge pressure zone is prohibited;
- said second position is an open position where fluid flow between said discharge
chamber (80) and said discharge pressure zone is permitted at a first flow level;
- said machine being characterized by:
- a biasing member (138) urging said discharge valve (130) toward said first and
second positions such that said discharge valve (130) is operable in a third
position when said biasing member (138) is overcome;
- said third position is an open position where fluid flow between said discharge
chamber (80) and said discharge pressure zone is permitted at a second flow
level greater than said first flow level.

2. The scroll machine (10) as claimed in claim 1, wherein said discharge valve (130)
moves axially with respect to said first scroll member (70).
3. The scroll machine (10) as claimed in claim 1, wherein fluid flows around an outer
periphery of said discharge valve (130) when said discharge valve (130) is in said third
position.

4. The scroll machine (10) as claimed in claim 1, wherein a passage (76) between said
first scroll member (70) and said discharge valve (130) is opened when said discharge
valve (130) moves from said second position to said third position.
5. The scroll machine (10) as claimed in claim 1, wherein said discharge valve (130)
comprises a valve plate (134) and a valve stop (136).
6. The scroll machine (10) as claimed in claim 5, wherein said valve plate (134) moves
with respect to said valve stop (136) when said discharge valve (130) moves from said
first position to said third position.
7.* The scroll machine (10) as claimed in claim 5, wherein said valve plate (134) moves
with respect to said first scroll member (70) when said discharge valve (130) moves
from said second position to said third position.
8. The scroll machine (10) as claimed in claim 1, wherein said discharge valve (130)
comprises a valve seat (132) and a valve plate (134).
9. The scroll machine (10) as claimed in claim 8, wherein said valve plate (134) moves
with respect to said valve seat (132) when said discharge valve (130) moves from said
first position to said second position.

10.The scroll machine (10) as claimed in claim 8, wherein said valve plate (134) moves
with respect to said first scroll member (70) when said discharge valve (130) moves
from said second position to said third position.
11. The scroll machine (10) as claimed in claim 1, wherein said discharge valve (130)
comprises a valve seat (132), a valve plate (134) and a valve stop {136).
12.The scroll machine (10) as claimed in claim 11, wherein said biasing member (138) is
arranged to urge said valve seat (132), valve plate (134) and valve stop (136) move
when said biasing member (138) is overcome to allow operation in said third position.
13.The scroll machine (10) as claimed in claim 12, wherein said biasing member (138) is a
wave washer.
14.The scroll machine (10) as claimed in claim 1, further comprising a shell (12, 14), said
first and second scroll members (70, 56) being disposed in said shell (12,14).
15.The scroll machine (10) as claimed in claim 14, wherein said shell (12, 14) defines a
portion of said discharge chamber (80).

16. A scroll machine (10) comprising:
- a shell (12,14) defining a discharge chamber (80);
- a first scroll member (70) having a first spiral wrap (72) projecting
outwardly from a first end cap (74);
- a second scroll member (56) having a second spiral wrap (58) projecting
outwardly from a second end cap (60), said second spiral wrap (58) being
intermeshed with said first spiral wrap (72);
- a drive member (28) for causing said scroll members (70, 56) to orbit
relative to one another whereby said spiral wraps (72, 58) will create
pocket of progressively changing volume between a suction pressure zone
and a discharge pressure zone, said discharge pressure zone being in
communication with said discharge chamber (80); and
- a discharge valve assembly (130) disposed between said discharge
pressure zone and said discharge chamber (80);
- said machine being characterized by:
- said discharge valve assemble being axially movable relative to said first
scroll member (70), said discharge valve assemble (130) including a valve
plate (134) deflectable between a first open state and a closed state.
17.The scroll machine (10) as claimed in claim 16, wherein said valve plate (134) is
normally in said first open state.

18.The scroll machine (10) as claimed in claim 16, wherein said discharge valve
assemble (130) is disposed within a recess (78) formed by said first scroll
member (70).
19.The scroll machine (10) as claimed in claim 16, wherein said discharge valve
assemble (130) further comprises a valve seat (132) and a valve stop (136).
20.The scroll machine (10) as claimed in claim 19, wherein said valve plate (134)
moves with respect to said valve seat (132) and said valve stop (136) between
said first open state and said closed state.
21.The scroll machine (10) as claimed in claim 19, wherein said valve plate (134)
engages said valve seat (132) when said valve plate (134) is in said closed state.
22.The scroll machine (10) as claimed in claim 19, wherein said valve plate (134) is
movable into a second open state.
23.The scroll machine (10) as claimed in claim 22, wherein said valve plate (134)
abuts said valve stop (136) in said second open state.

24. The scroll machine (10) as claimed in claim 16, further comprising a biasing
member (138) applying a force on said discharge valve assembly (130) to bias
said discharge valve assembly (130) in a first direction relative to said first scroll
member (70).
25.The scroll machine (10) as claimed in claim 24, wherein said discharge valve
assembly (130) is movable in a second direction opposite to said first direction
and against said force of said biasing member (138).
26. The scroll machine (10) as claimed in claim 16, wherein said discharge valve
assembly (130) biased into engagement with said first scroll member (70).
*
27.The scroll machine (10) as claimed in claim 16, wherein said discharge valve
assembly (130) is movable between a first position and a second position relative
to said first scroll member (70), said valve plate (134) permitting communication
between said discharge pressure zone and said discharge chamber (80) when
said discharge valve assembly (130) is in either said first position or said second
position and restricting communication between said discharge pressure zone
and said discharge chamber (80) when said valve plate (134) is in said closed
state and said discharge valve assembly (130) is in said second position.

28.The scroll machine (10) as claimed in claim 27, wherein said discharge valve
assembly (130) abuts a surface of said first scroll member (70) in said second
position.
29.The scroll machine (10) as claimed in claim 27, further comprising a biasing
member (138) biasing said discharge valve assembly (130) into said second
position.
30.The scroll machine (10) as claimed in claim 27, wherein said discharge valve
assembly (130) is biased into said second position.

31.The scroll machine (10) as claimed in claim 16, wherein said discharge valve
assembly (130) and said valve plate (134) cooperate to define a first open state,
a second open state, a third open state, and a closed state.
32.The scroll machine (10) as claimed in claim 31, wherein said first open state,
second open state, and said third open state provide three different flow levels
between said discharge pressure zone and said discharge chamber (80) and said
closed state restricts flow between said discharge pressure zone and said
discharge chamber (80).

33. A scroll machine (10) comprising:
- a shell (12,14) defining a chamber (80);
- a first scroll member (70) having a first spiral wrap (72) projecting
outwardly from a first end cap (74);
- a second scroll member (56) having a second spiral wrap (58) projecting
outwardly from a second end cap (60), said second spiral wrap (58) being
intermeshed with said first spiral wrap (72);
- a drive member (28) for causing said scroll member (70, 56) to orbit
relative to one another whereby said spiral wraps (72, 58) will create
pockets of progressively changing volume between a suction pressure
zone and a discharge pressure zone, said discharge pressure zone being
in communication with said discharge chamber (80), and
- a discharge valve assembly (130) disposed between said discharge
pressure zone and said discharge chamber (80);
- said machine being characterized by:
- said discharge valve assembly (130) being disposed within a recess (78)
formed by said first scroll member (70), said discharge valve assembly
(130) being movable between a first, a second, and a thirds position,
wherein:
- said first position is a closed position where said discharge valve assembly
(130) abuts a bottom surface of said recess (78) and fluid flow between

- said discharge chamber and said discharge pressure zone is prohibited;
- said second position is an open position where said discharge valve
assembly (130) abuts said bottom surface of said recess (78) and fluid
flow between said discharge chamber (80) and said discharge pressure
zone is permitted at a first flow level; and
- said third position is an open position where said discharge valve
assembly (130) is spaced from said bottom surface of said recess (78) and
fluid flow between said discharge chamber and said discharge pressure
zone is permitted at a second flow level greater than said first flow level.
34.The scroll machine (10) as claimed in claim 33, wherein said discharge valve
assembly (130)'moves axially with respect to said first scroll mem6er (70).
35.The scroll machine (10) as claimed in claim 33, wherein fluid flows around an
outer periphery of said discharge valve assembly (130) when said discharge
valve assembly (130) is in said third position.
36.The scroll machine (10) as claimed in claim 33, wherein a passage between said
first scroll member (70) and said discharge valve assembly (130) is opened when
discharge valve assembly (130) moves from said second position to said third
position.

37.The scroll machine (10) as claimed in claim 33, wherein said discharge valve
assembly (130) comprises a valve plate (134) and a valve stop (136).
38.The scroll machine (10) as claimed in claim 37, wherein said valve plate (134)
moves with respect to said valve stop (136) when discharge valve assembly
(130) moves from said first position to said third position.
39.The scroll machine (10) as claimed in claim 37, wherein said valve plate (134)
moves with respect to said first scroll member (70) when said discharge valve
assembly (130) moves from said second position to said third position.
40.The scroll machine (10) as claimed in claim 33, wherein said discharge valve
assembly (130) comprises a valve seat (132) and a valve plate (134).
41.The scroll machine (10) as claimed in claim 40, wherein said valve plate (134)
moves with respect to said valve seat (132) when said discharge valve assembly
moves from said first position to said second position.

42. The scroll machine (10) as claimed in claim 40, wherein said valve plate (134)
moves with respect to said first scroll member (70) when said discharge valve
assembly (130) moves from said second position to said third position.
43. The scroll machine (10) as claimed in claim 33, wherein said discharge valve
assembly (130) comprises a valve seat (132), a valve plate (134) and a valve
stop (136).


A compressor (10) includes a normally open discharge valve assembly (130) for
controlling compressed refrigerant flow from the discharge chamber (80) through the
compression members (56, 70). This controlling of flow results in an increased
performance for the compressor (10) by reducing recompression volume and the
elimination of reverse rotation at shut down. The discharge valve assembly (130)
includes a valve seat (132), a valve plate (134) and a valve stop (136) secured within a
recess (78) formed within the compressor (10) with a wave ring retainer (138). The
valve stop (136) and the valve seat (132) include a contoured surface that is engaged
by the valve plate (134) when it opens and closes. The contoured surface controls the
movement of the valve plate (134).

Documents:

457-KOL-2004-ASSIGNMENT.pdf

457-kol-2004-assignment1.1.pdf

457-KOL-2004-CORRESPONDENCE 1.2.pdf

457-KOL-2004-CORRESPONDENCE 1.3.pdf

457-KOL-2004-CORRESPONDENCE-1.1.pdf

457-KOL-2004-CORRESPONDENCE.pdf

457-kol-2004-correspondence1.4.pdf

457-kol-2004-examination report.pdf

457-kol-2004-form 1.pdf

457-KOL-2004-FORM 13-1.1.pdf

457-KOL-2004-FORM 13.pdf

457-kol-2004-form 18.pdf

457-kol-2004-form 26.pdf

457-KOL-2004-FORM 3.pdf

457-kol-2004-form 5.pdf

457-kol-2004-form 6.pdf

457-KOL-2004-FORM-27.pdf

457-kol-2004-gpa.pdf

457-kol-2004-granted-abstract.pdf

457-kol-2004-granted-abstract1.1.pdf

457-kol-2004-granted-assignment.pdf

457-kol-2004-granted-claims.pdf

457-kol-2004-granted-claims1.1.pdf

457-kol-2004-granted-correspondence.pdf

457-kol-2004-granted-description (complete).pdf

457-kol-2004-granted-description (complete)1.1.pdf

457-kol-2004-granted-drawings.pdf

457-kol-2004-granted-drawings1.1.pdf

457-kol-2004-granted-examination report.pdf

457-kol-2004-granted-form 1.1.pdf

457-kol-2004-granted-form 1.pdf

457-kol-2004-granted-form 13.pdf

457-kol-2004-granted-form 18.pdf

457-kol-2004-granted-form 2.1.pdf

457-kol-2004-granted-form 2.pdf

457-kol-2004-granted-form 3.pdf

457-kol-2004-granted-form 5.pdf

457-kol-2004-granted-form 6.pdf

457-kol-2004-granted-gpa.pdf

457-kol-2004-granted-reply to examination report.pdf

457-kol-2004-granted-specification.pdf

457-kol-2004-granted-specification1.1.pdf

457-kol-2004-granted-translated copy of priority document.pdf

457-KOL-2004-OTHERS 1.1.pdf

457-KOL-2004-OTHERS.pdf

457-kol-2004-others1.2.pdf

457-KOL-2004-PA.pdf

457-kol-2004-reply to examination report.pdf


Patent Number 248476
Indian Patent Application Number 457/KOL/2004
PG Journal Number 29/2011
Publication Date 22-Jul-2011
Grant Date 18-Jul-2011
Date of Filing 30-Jul-2004
Name of Patentee EMERSON CLIMATE TECHNOLOGIES, INC.
Applicant Address 1675 W. CAMPBELL ROAD, SIDNEY OHIO
Inventors:
# Inventor's Name Inventor's Address
1 PEYTON, JESSE 1150 VAN WAY, PIQUA, OHIO 45356
PCT International Classification Number F01C 1/02, F04C 2/00
PCT International Application Number N/A
PCT International Filing date
PCT Conventions:
# PCT Application Number Date of Convention Priority Country
1 10/671,049 2003-09-25 U.S.A.