U.S. patent application number 11/145187 was filed with the patent office on 2006-03-09 for refrigerating system for refrigerator.
Invention is credited to Sam Chul Ha, Jun Hyun Hwang, Sung Hee Kang, Hyeon Kim, Jong Kwon Kim, Jong Min Shin.
Application Number | 20060048528 11/145187 |
Document ID | / |
Family ID | 35994847 |
Filed Date | 2006-03-09 |
United States Patent
Application |
20060048528 |
Kind Code |
A1 |
Shin; Jong Min ; et
al. |
March 9, 2006 |
Refrigerating system for refrigerator
Abstract
Refrigerating system for a refrigerator including a variable
capacity compressor having a varied rate of compressed refrigerant
delivery for compressing refrigerant, a condenser for condensing
the refrigerant compressed by the variable capacity compressor, a
freezing chamber expansion valve for expanding condensed
refrigerant, a freezing chamber evaporator for cooling air by using
the refrigerant supplied from the freezing chamber expansion valve,
two or more than two refrigerating chamber expansion valves having
different lengths of refrigerant flow passages, for expanding the
condensed refrigerant, two or more than two refrigerating chamber
evaporators having different lengths of refrigerant flow passages,
for cooing air by using the refrigerant from the refrigerating
chamber expansion valves, respectively, and a distributor between
the condenser and the expansion valves for selective supply of the
refrigerant to the expansion valves according to an operation time
period of the refrigerating system, thereby providing a
refrigerating system for a refrigerator having a high
efficiency.
Inventors: |
Shin; Jong Min; (Busan,
KR) ; Kim; Hyeon; (Gyeongsangnam-do, KR) ;
Kang; Sung Hee; (Gyeongsangnam-do, KR) ; Hwang; Jun
Hyun; (Gyeongsangnam-do, KR) ; Kim; Jong Kwon;
(Gyeongsangnam-do, KR) ; Ha; Sam Chul;
(Gyeongsangnam-do, KR) |
Correspondence
Address: |
FLESHNER & KIM, LLP
P.O. BOX 221200
CHANTILLY
VA
20153
US
|
Family ID: |
35994847 |
Appl. No.: |
11/145187 |
Filed: |
June 6, 2005 |
Current U.S.
Class: |
62/222 ;
62/228.1; 62/527 |
Current CPC
Class: |
F25B 41/385 20210101;
Y02B 40/00 20130101; F25B 2500/26 20130101; F25B 2600/02 20130101;
F25B 5/00 20130101; F25B 2600/23 20130101; F25D 11/022 20130101;
F25B 2600/2511 20130101 |
Class at
Publication: |
062/222 ;
062/228.1; 062/527 |
International
Class: |
F25B 41/04 20060101
F25B041/04; F25B 49/00 20060101 F25B049/00; F25B 41/06 20060101
F25B041/06; F25B 1/00 20060101 F25B001/00 |
Foreign Application Data
Date |
Code |
Application Number |
Jan 6, 2004 |
KR |
2004-00622 |
Claims
1. A refrigerating system for a refrigerator comprising: a variable
capacity compressor having a varied rate of compressed refrigerant
delivery for compressing refrigerant; a condenser for condensing
the refrigerant compressed by the variable capacity compressor; a
freezing chamber expansion valve for expanding condensed
refrigerant; a freezing chamber evaporator for cooling air by using
the refrigerant supplied from the freezing-chamber expansion valve;
two or more than two refrigerating chamber expansion valves having
different lengths of refrigerant flow passages, for expanding the
condensed refrigerant; two or more than two refrigerating chamber
evaporators having different lengths of refrigerant flow passages,
for cooing air by using the refrigerant from the refrigerating
chamber expansion valves, respectively; and a distributor between
the condenser and the expansion valves for selective supply of the
refrigerant to the expansion valves according to an operation time
period of the refrigerating system.
2. The refrigerating system as claimed in claim 1, wherein the
refrigerating chamber expansion valve includes; a first
refrigerating chamber expansion valve having a relatively short
refrigerant flow passage, and a second refrigerating chamber
expansion valve having a relatively long refrigerant flow
passage.
3. The refrigerating system as claimed in claim 1, further
comprising a guide valve for selective supply of the refrigerant to
one of the refrigerating chamber expansion valves.
4. The refrigerating system as claimed in claim 1, wherein the
refrigerating chamber evaporator includes; a first refrigerating
chamber evaporator having a relatively long refrigerant flow
passage, and a second refrigerating chamber evaporator having a
relatively short refrigerant flow passage.
5. The refrigerating system as claimed in claim 4, further
comprising a bypass valve at an inlet of the second refrigerating
chamber evaporator for selective supply of the refrigerant passed
through the first refrigerating chamber evaporator to the second
refrigerating chamber evaporator.
6. The refrigerating system as claimed in claim 1, wherein the
expansion valves and the evaporators are configured to form a
relatively short refrigerant flow passage when the refrigerating
system is put into operation.
7. The refrigerating system as claimed in claim 1, wherein the
variable capacity compressor has a relatively high rate of
compressed refrigerant delivery when the refrigerating system
starts operation.
8. The refrigerating system as claimed in claim 1, wherein the
distributor supplies the refrigerant only to the freezing chamber
expansion valve and the freezing chamber evaporator when the
refrigerating system starts operation.
9. The refrigerating system as claimed in claim 8, wherein the
refrigerant is supplied to the refrigerating chamber expansion
valve having the relatively short flow passage through the
distributor additionally when the refrigerating system starts
operation.
10. The refrigerating system as claimed in claim 1, wherein the
expansion valves and the evaporators are configured to form a
relatively longer refrigerant flow passage than the refrigerant
flow passage at the time of starting the refrigerating system when
a preset time period is passed after starting of the refrigerating
system.
11. The refrigerating system as claimed in claim 1, wherein the
variable capacity compressor has a relatively low rate of
compressed refrigerant delivery when the preset time period is
passed after starting of the refrigerating system.
12. The refrigerating system as claimed in claim 1, wherein the
refrigerant is supplied to the freezing chamber expansion valve and
the refrigerating chamber expansion valve having the relatively
long flow passage through the distributor when the preset time
period is passed after starting of the refrigerating system.
13. The refrigerating system as claimed in claim 1, wherein the
refrigerant is supplied to all of the refrigerating chamber
evaporators when a preset time period is passed after starting of
the refrigerating system.
Description
BACKGROUND OF THE INVENTION
[0001] 1. Field of the Invention
[0002] The present invention relates to refrigerating systems for
refrigerators, and more particularly, to a method for controlling
operation of a refrigerating system.
[0003] 2. Discussion of the Related Art
[0004] In general, the refrigerator cools a space thereof for fresh
storage of food therein for a time period while refrigerant
(working fluid) repeats a refrigerating cycle of
compression-condensing-expansion-evaporation.
[0005] Of the refrigerators, a direct cooling type refrigerator is
provided with separate evaporators for a freezing chamber and a
refrigerating chamber respectively. The direct cooling type
refrigerator will be described in detail with reference to FIG.
1.
[0006] The refrigerating system of the direct cooling type
refrigerator is provided with a compressor 11, a condenser 12, an
expansion valve 13, a freezing chamber evaporator 14, and a
refrigerating chamber evaporator 15. Various units of the
refrigerating system are connected with refrigerant pipes 16.
[0007] The compressor 11 compresses low temperature/low pressure
refrigerant gas to high temperature/high pressure refrigerant gas.
The condenser 12 receives and compresses refrigerant from the
compressor 11. The expansion valve 13 receives refrigerant from the
condenser 12 and drops a pressure of the refrigerant. The freezing
chamber evaporator 14 and the refrigerating evaporator 15 evaporate
the refrigerant from the expansion valve 13 in a low pressure
state, to absorb heat from air in the vicinity of the evaporators
14, and 15. Air cooled down by the evaporators 14, and 15 is
supplied to the freezing chamber and the refrigerating chamber for
fresh storage of food. Above cycle is repeated continuously while
the refrigerator is operated.
[0008] However, as shown, because of the separate freezing chamber,
and refrigerating chamber evaporators 14, and 15, the refrigerating
system for a refrigerator has a substantially long total
refrigerant flow passage of the refrigerant pipes 16 and other
components (evaporators, expansion valves, and so on). For this
reason, though the refrigerating system requires a high flow rate
of refrigerant when the refrigerating system starts operation, the
refrigerating system requires a relatively low flow rate once
operation of the refrigerating system is stabilized after a certain
time period passes. Such a flow rate of the refrigerant in such a
system is substantially dependent on a rate of compressed
refrigerant delivery of the compressor and a length of the flow
passage of the refrigerant. However, since the related art
refrigerating system has a fixed rate of compressed refrigerant
delivery of the compressor and a fixed total refrigerant flow
passage, the related art refrigerating system consumes power
unnecessarily, resulting to have a low operation efficiency.
SUMMARY OF THE INVENTION
[0009] Accordingly, the present invention is directed to a
refrigerating system for a refrigerator that substantially obviates
one or more problems due to limitations and disadvantages of the
related art.
[0010] An object of the present invention is to provide a
refrigerating system for a refrigerator which has a low power
consumption and a high efficiency.
[0011] Additional advantages, objects, and features of the
invention will be set forth in part in the description which
follows and in part will become apparent to those having ordinary
skill in the art upon examination of the following or may be
learned from practice of the invention. The objectives and other
advantages of the invention may be realized and attained by the
structure particularly pointed out in the written description and
claims hereof as well as the appended drawings.
[0012] To achieve these objects and other advantages and in
accordance with the purpose of the invention, as embodied and
broadly described herein, a refrigerating system for a refrigerator
includes a variable capacity compressor having a varied rate of
compressed refrigerant delivery for compressing refrigerant, a
condenser for condensing the refrigerant compressed by the variable
capacity compressor, a freezing chamber expansion valve for
expanding condensed refrigerant, a freezing chamber evaporator for
cooling air by using the refrigerant supplied from the freezing
chamber expansion valve, two or more than two refrigerating chamber
expansion valves having different lengths of refrigerant flow
passages, for expanding the condensed refrigerant, two or more than
two refrigerating chamber evaporators having different lengths of
refrigerant flow passages, for cooing air by using the refrigerant
from the refrigerating chamber expansion valves, respectively, and
a distributor between the condenser and the expansion valves for
selective supply of the refrigerant to the expansion valves
according to an operation time period of the refrigerating
system.
[0013] The refrigerating chamber expansion valve includes a first
refrigerating chamber expansion valve having a relatively short
refrigerant flow passage, and a second refrigerating chamber
expansion valve having a relatively long refrigerant flow passage.
In this case, the refrigerating system further includes a guide
valve for selective supply of the refrigerant to one of the
refrigerating chamber expansion valves.
[0014] The refrigerating chamber evaporator includes a first
refrigerating chamber evaporator having a relatively long
refrigerant flow passage, and a second refrigerating chamber
evaporator having a relatively short refrigerant flow passage. In
this case, the refrigerating system further includes a bypass valve
at an inlet of the second refrigerating chamber evaporator for
selective supply of the refrigerant passed through the first
refrigerating chamber evaporator to the second refrigerating
chamber evaporator.
[0015] Preferably, the expansion valves and the evaporators are
configured to form a relatively short refrigerant flow passage, and
has a relatively high rate of compressed refrigerant delivery when
the refrigerating system starts operation. The distributor supplies
the refrigerant only to the freezing chamber expansion valve and
the freezing chamber evaporator when the refrigerating system
starts operation. The refrigerant is supplied to the refrigerating
chamber expansion valve having the relatively short flow passage
through the distributor additionally when the refrigerating system
starts operation.
[0016] The expansion valves and the evaporators are configured to
form a relatively longer refrigerant flow passage than the
refrigerant flow passage at the time of starting the refrigerating
system, and the variable capacity compressor has a relatively low
rate of compressed refrigerant delivery when the preset time period
is passed after starting of the refrigerating system.
[0017] The refrigerant is supplied to the freezing chamber
expansion valve and the refrigerating chamber expansion valve
having the relatively long flow passage through the distributor
when the preset time period is passed after starting of the
refrigerating system. Moreover, the refrigerant is supplied to all
of the refrigerating chamber evaporators when a preset time period
is passed after starting of the refrigerating system.
[0018] Thus, the refrigerating system of the present invention
consumes less power and has a high efficiency.
[0019] It is to be understood that both the foregoing general
description and the following detailed description of the present
invention are exemplary and explanatory and are intended to provide
further explanation of the invention as claimed.
BRIEF DESCRIPTION OF THE DRAWINGS
[0020] The accompanying drawings, which are included to provide a
further understanding of the invention and are incorporated in and
constitute a part of this application, illustrate embodiment(s) of
the invention and together with the description serve to explain
the principle of the invention. In the drawings;
[0021] FIG. 1 illustrates a diagram of a related art refrigerating
system for a refrigerator, schematically;
[0022] FIG. 2 illustrates a diagram of a refrigerant flow in a
refrigerating system for a refrigerator of the present invention
when a compressor thereof is operated in a power mode;
[0023] FIG. 3 illustrates a diagram of a modification of a
refrigerant flow in a refrigerating system for a refrigerator of
the present invention when a compressor thereof is operated in a
power mode; and
[0024] FIG. 4 illustrates a diagram of a refrigerant flow in a
refrigerating system for a refrigerator of the present invention
when a compressor thereof is operated in a saving mode.
DETAILED DESCRIPTION OF THE INVENTION
[0025] Reference will now be made in detail to the preferred
embodiments of the present invention, examples of which are
illustrated in the accompanying drawings. Wherever possible, the
same reference numbers will be used throughout the drawings to
refer to the same or like parts.
[0026] FIGS. 2 and 3 illustrate diagrams of a refrigerant flow in a
refrigerating system for a refrigerator of the present invention,
and a modification thereof respectively when a compressor thereof
is operated in a power mode. FIG. 4 illustrates a diagram of a
refrigerant flow in a refrigerating system for a refrigerator of
the present invention when a compressor thereof is operated in a
saving mode.
[0027] The refrigerating system for a refrigerator of the present
invention includes a compressor 100, a condenser 200, a freezing
chamber expansion valve 310, two or more than two refrigerating
chamber expansion valves 321, and 322, freezing chamber evaporator
400, two or more than two refrigerating chamber evaporators 510,
and 520, and a refrigerant distributor 700. Above units are
connected with a refrigerant pipe 600 for enabling refrigerant
flow.
[0028] The compressor 100 is a variable capacity compressor which
can vary a rate of compressed refrigerant delivery. The variable
capacity compressor may be a dual capacity compressor which has
different rates of compressed refrigerant delivery depending on a
direction of rotation of a motor thereof. The Korea Patent
Application No. 10-2001-0064083 discloses one example of the dual
capacity compressor. Moreover, the variable capacity compressor 100
may be a multi-capacity compressor which has a rate of compressed
refrigerant delivery varied with a rotation speed of a motor by an
inverter. Other than above examples, various types of variable
capacity compressors are applicable to the present invention.
[0029] The condenser 200 receives and condenses compressed
refrigerant from the variable capacity compressor 100, and has a
configuration the same with a general condenser.
[0030] The freezing chamber expansion valve 310 reduces a pressure
of the refrigerant condensed at the condenser 200, and provides to
the freezing chamber evaporator 400.
[0031] The refrigerating chamber evaporators 510, and 520 are a
first refrigerating chamber evaporator 510 having a relatively long
refrigerant flow passage, and a second refrigerating chamber
evaporator 520 having a relatively short refrigerant flow passage.
The first refrigerating chamber evaporator 510 has a greater
cooling capacity compared to the second refrigerating chamber
evaporator 520 owing to the relatively long refrigerant flow
passage. Therefore, the first refrigerating chamber evaporator 510
is mounted in a main refrigerating chamber for storage of food, and
the second refrigerating chamber evaporator 520 is mounted in a
supplementary refrigerating chamber, such as a vegetable chamber,
which requires a relatively high storage temperature.
[0032] Moreover, both an inlet and an outlet of the second
refrigerating chamber evaporator 520 are connected to an outlet of
the first refrigerating chamber evaporator 510. A bypass valve 810
is mounted at the inlet of the second refrigerating chamber
evaporator 520 for making the refrigerant, passed through the first
refrigerating chamber evaporator 510, to bypass the second
refrigerating chamber evaporator 520. the Outlets of the
refrigerating chamber evaporators 510, and 520 join with the outlet
of the freezing chamber evaporator 400 in a state connected with
each other. The refrigerant from the evaporators 400, 510, and 520
is supplied to the variable capacity compressor 100.
[0033] The refrigerating chamber expansion valve 321, or 322 drops
a pressure of the refrigerant condensed at the condenser 200, and
provides to the first refrigerating chamber evaporator 510. The
refrigerating chamber expansion valve s 321, and 322 are a first
refrigerating chamber expansion valve 321 having a relatively short
refrigerant flow passage, and a second refrigerating chamber
expansion valve 322 having a relatively long refrigerant flow
passage. An inlet and an outlet of the first refrigerating chamber
expansion valve 321 are connected to an inlet and an outlet of the
second refrigerating chamber expansion valve 322, respectively. A
guide valve 820 is mounted between the inlet of the second
refrigerating chamber expansion valve 322 and the inlet of the
first refrigerating chamber expansion valve 321, for supplying
refrigerant to one of the first, and second refrigerating chamber
expansion valve 321, and 322, selectively.
[0034] The distributor 700 is mounted in the refrigerant pipe 600
between the condenser 200 and the expansion valves 310, 321, and
322. The distributor 700 selectively provides refrigerant to the
freezing chamber expansion valve 310, and the refrigerating chamber
expansion valve 321, and 322 according to an operation time period
of the refrigerating system. In more detail, the distributor
supplies refrigerant only to the freezing chamber expansion valve
310 at an initial stage of operation of the refrigerating system.
If a preset time period passes after starting of operation, the
distributor 700 supplies refrigerant to the freezing chamber
expansion valve 310 as well as the refrigerating chamber expansion
valve 321, and 322. Alternatively, if the refrigerating chamber
evaporators 510 and 520 are not required to use, for an example, in
winter when an environmental temperature is low, the distributor
700 may not supply refrigerant to the refrigerating chamber
expansion valves 321, and 322 for making the refrigerating chamber
evaporators 510, and 520 inoperative.
[0035] The operation steps of the refrigerating system for a
refrigerator of the present invention will be described with
reference to related drawings in more detail.
[0036] Referring to FIGS. 2 and 3, upon putting the refrigerating
system into operation, the variable capacity compressor 100 is
operated in the power mode. The power mode is a mode in which the
variable capacity compressor 100 exerts a relatively great rate of
compressed refrigerant delivery, preferably, the greatest rate of
compressed refrigerant delivery. As described, since the
refrigerating system has a substantially long refrigerant flow
passage, it is required that a large quantity of refrigerant flows
in the refrigerating system for stabilize operation of the
refrigerating system as soon as possible when the refrigerating
system starts to operate. Accordingly, when the refrigerating
system is put into operation, the variable capacity compressor is
operated in the power mode for supplying a large quantity of
refrigerant to the system.
[0037] Moreover, as known, the torque and voltage required for
starting the compressor 110 is dependent on a flow rate of the
refrigerant required for starting the refrigerant system, and the
flow rate can be varied with a length of the refrigerant flow
passage. That is, the torque and voltage of the compressor is
dependent on the length of the refrigerant flow passage. Therefore,
when operation of the refrigerating system is started, i.e., when
the compressor is started, the expansion valves 310, 321, and 322
and the evaporators 400, 510, and 520 are configured to form a
relatively short flow passage for reducing the starting torque and
voltage of the compressor. In more detail, as shown in FIG. 3, at
an initial starting of the refrigerating system, the distributor
700 cuts off the refrigerant flow to the refrigerating chamber
evaporators 510, and 520, more specifically, the refrigerating
chamber expansion valves 321, and 322. That is, the distributor 700
supplies refrigerant only to the freezing chamber expansion valve
310 and the freezing chamber evaporator 400, to shorten the
refrigerant flow passage in the refrigerating system substantially,
accordingly. That is, because the refrigerant flows, not to the
refrigerating chamber expansion valves 321, and 322 and the
refrigerating chamber evaporators 510, and 520, but only to the
freezing chamber expansion valve 310 and the freezing chamber
evaporator 400, a total flow passage is shortened substantially.
According to this, the torque required for the initial starting of
the compressor 110 is reduced to the maximum in proportion to the
shortened refrigerant flow passage and the reduced flow rate.
Moreover, the shortened refrigerant flow passage is effective for
fast stabilization of the refrigerating system.
[0038] To shorten the refrigerant flow passage, instead of the
freezing chamber expansion valve 310 and the freezing chamber
evaporator 400, the refrigerant may be supplied to the
refrigerating chamber expansion valves 321, and 322 and the
refrigerating chamber evaporators 510, and 520. However, in
general, since it is required that a temperature of the freezing
chamber is maintained lower than a temperature of the refrigerating
chamber, it is required that expanded refrigerant is supplied to
the freezing chamber evaporator 140 at first. Under this reason, it
is not preferable to cut off an initial refrigerant supply to the
freezing chamber evaporator 140 for stable operation of the
refrigerating system. Therefore, as described, the cutting off of
the initial refrigerant supply to the refrigerating chamber
evaporator 150 is advantageous both in view of reducing the
refrigerant circulating distance, and making the refrigerating
system operation stable.
[0039] Alternatively, when the refrigerating system is started, the
first refrigerating chamber evaporator 510 may be started in
addition to the freezing chamber evaporator 400. In more detail, as
shown in FIG. 2, the distributor 700 supplies the refrigerant both
to the freezing chamber expansion valve 310 and the refrigerating
chamber expansion valves 321, and 322. However, for shortening the
refrigerant flow passage, the guide valve 820 supplies refrigerant
only to the first expansion valve 321 having a relatively short
flow passage, to supply the refrigerant to the first refrigerant
evaporator 510 through the first refrigerant chamber expansion
valve 321. The refrigerant bypasses the second refrigerant
evaporator 520 by the bypass valve 810 for shortening the
refrigerant flow passage. As described before, the first
refrigerant chamber evaporator 510 cools down the main
refrigerating chamber. Therefore, such an additionally operation of
the first refrigerating chamber enables to shorten the refrigerant
flow passage to some extent for reducing the initial torque of the
compressor 100, and, at the same time with this, stabilize an
entire refrigerating system, quickly.
[0040] Referring to FIG. 4, as described, if the entire
refrigerating system is stabilized after operation for a certain
time period, the variable capacity compressor 100 is operated in a
saving mode. The saving mode is a mode in which the variable
capacity compressor 100 can deliver a rate of compressed
refrigerant which is lower than a rate of compressed refrigerant
the variable capacity compressor 100 delivers in the power mode,
but can prevent operation efficiency of the entire refrigerating
system from dropping. Once stabilized, the refrigerating system
requires a relatively lower rate of refrigerant. Therefore, if a
preset time period is passed after the refrigerating system is
started, the variable capacity compressor 100 is operated in the
saving mode so as to deliver a relatively smaller rate of
compressed refrigerant to the system.
[0041] Moreover, since the smaller rate of compressed refrigerant
is supplied in the saving mode, it is required to provide the
longest refrigerant flow passage for obtaining the highest heat
exchange efficiency. Accordingly, the expansion valves 310, 321,
and 322 and the evaporators 400, 510, and 520 are configured to
form the longest flow passage for obtaining the highest efficiency.
In more detail, as shown in FIG. 4, the distributor 700 supplies
refrigerant both to the freezing chamber expansion valve 310 and
the refrigerating chamber expansion valves 321, and 322. However,
for increasing the refrigerant flow passage, the guide valve 820
supplies refrigerant to the second expansion valve 322 having a
relatively long flow passage, to supply the refrigerant to the
first refrigerating chamber evaporator 510 through the second
refrigerating chamber expansion valve 321. Moreover, in order to
increase the refrigerant flow passage, the refrigerant is supplied
to the second refrigerant chamber evaporator 520 by the bypass
valve 810. Therefore, the refrigerant passes through, not only the
freezing chamber evaporator 400, but also the first, and second
refrigerating camber evaporators 510, and 520. According to this,
the length of the refrigerant flow passage is maximized, to obtain
the highest heat exchange efficiency even with a small flow rate of
compressed refrigerant.
[0042] As has been described, in the present invention, upon
starting the refrigerating system, the variable capacity compressor
delivers a high flow rate of compressed refrigerant, and a
refrigerant flow passage is shortened, for stabilizing the
refrigerating system quickly, and reducing a starting toque and a
starting voltage of the compressor. Moreover, once the
refrigerating system is stabilized, the variable capacity
compressor delivers a relatively small rate of compressed
refrigerant for obtaining a high efficiency, and the refrigerant
flow passage is extended. Thus, the refrigerating system of the
present invention optimizes the flow rate of compressed refrigerant
and the refrigerant flow passage taking an operation time period
and an operation state into account, thereby consuming power less
and obtaining a high efficiency.
[0043] It will be apparent to those skilled in the art that various
modifications and variations can be made in the present invention
without departing from the spirit or scope of the inventions. Thus,
it is intended that the present invention covers the modifications
and variations of this invention provided they come within the
scope of the appended claims and their equivalents.
* * * * *