U.S. patent number 3,640,085 [Application Number 05/133,038] was granted by the patent office on 1972-02-08 for refrigeration system with delay timing mechanism.
This patent grant is currently assigned to Deltrol Corp.. Invention is credited to John L. Harris.
United States Patent |
3,640,085 |
Harris |
February 8, 1972 |
REFRIGERATION SYSTEM WITH DELAY TIMING MECHANISM
Abstract
Protection against refrigeration compressor burnout by short
cycling is provided by a delay timing mechanism having a motor and
solenoid. The motor is constantly energized and the solenoid
controlled by a thermostat stalls or releases the mechanism causing
timer operation through its cycle. The timer runs through its delay
period during the normal off period, allowing fast restart of the
compressor. Also the timer provides a longer delay following a
short cycle then following a normal cycle. This is accomplished by
operating the timer for a period of time after the compressor is
started.
Inventors: |
Harris; John L. (Delafield,
WI) |
Assignee: |
Deltrol Corp. (Bellwood,
IL)
|
Family
ID: |
26830977 |
Appl.
No.: |
05/133,038 |
Filed: |
April 12, 1971 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
|
|
849961 |
Aug 14, 1969 |
3598214 |
Aug 10, 1971 |
|
|
Current U.S.
Class: |
62/158; 62/231;
200/38R; 307/116; 318/484; 968/815 |
Current CPC
Class: |
G04F
3/06 (20130101); F25B 49/022 (20130101); F25B
2600/23 (20130101); F25B 2500/26 (20130101) |
Current International
Class: |
F25B
49/02 (20060101); G04F 3/06 (20060101); G04F
3/00 (20060101); F25b 019/00 () |
Field of
Search: |
;62/157,158,231 ;318/484
;200/38 ;307/116 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Perlin; Meyer
Parent Case Text
CROSS-REFERENCE TO RELATED APPLICATION
This application is a division of my application Ser. No. 849,961
filed Aug. 14, 1969, now U.S. Pat. No. 3,598,214 dated Aug. 10,
1971.
Claims
I claim:
1. In a control system for a refrigeration system having an
electric motor driven compressor, the combination of, a condition
responsive device, timing means including an electric timing motor
for driving the same and an electromagnet, a control circuit
including the condition responsive device and electromagnet whereby
the electromagnet is controlled by said condition responsive
device, an energizing circuit for the electric timing motor, said
energizing circuit being independent of said condition responsive
device, a switch for controlling the compressor motor, means
including the timing means and the electromagnet for closing said
switch in response to a call for condition change by the condition
responsive device, said timing means being arranged to delay
closure of said switch for a predetermined minimum time, means for
mechanically stopping said timing means at a point providing said
minimum time, said mechanical stopping means effectively stopping
the timing means even though the electric timing motor remains
energized by said independent energizing circuit, and means
controlled by the condition responsive device including said
electromagnet for rendering the mechanical stopping means
ineffective and opening said switch when the condition responsive
device calls for stopping the compressor.
2. The combination set forth in claim 1 in which a second condition
responsive means breaks the energizing circuit for the electric
timing motor and also deenergizes the electromagnet in response to
an unfavorable condition associated with the refrigeration system,
the duration of the unfavorable condition thus being added to said
predetermined minimum delay.
3. The combination set forth in claim 1 in which the timing means
provides a first delay period sufficient to allow equalization of
pressure in the refrigeration system and an additional delay period
in the event of a short cycle, said mechanical stopping means being
arranged to allow operation of the timing means following starting
of the compressor through said additional delay period and then to
stop said timing means.
4. The combination set forth in claim 3 in which a second condition
responsive means breaks the energizing circuit for the electric
timing motor and also deenergizes the electromagnet in response to
an unfavorable condition associated with the refrigeration system,
the duration of the unfavorable condition thus being added to the
delay provided by the timing means.
5. The combination set forth in claim 1 in which the refrigeration
system includes a blower having a blower motor therefore, and a
switch for the blower motor closed by said electromagnet in
response to call for condition change by the condition responsive
device.
6. In a control system for a refrigeration system having a
compressor and a blower, a compressor motor for driving the
compressor, a blower motor for driving the blower, a condition
responsive means, an electromagnet, a control circuit including the
condition responsive means and electromagnet whereby the condition
responsive means controls the electromagnet, means including a
compressor motor switch for controlling the compressor motor, means
including a blower motor switch for controlling the blower motor,
timing means including electric motor means, means for energizing
said electric motor means, means actuated by the electromagnet for
closing the blower motor switch on call for operation of the
compressor by the condition responsive means, means including the
timing means for causing closure of the compressor motor switch on
call for compressor operation by said condition responsive means,
said timing means being arranged to provide a delay between
successive energizations of the compressor motor, means for
stopping the timing means at a point providing said delay, means
operated by the electromagnet on call for stopping of the
compressor by the condition responsive means for opening the
compressor motor switch, and means also operated by the
electromagnet for rendering said stopping means ineffective,
allowing the timing means to proceed with a new cycle.
7. The combination recited in claim 6 in which the blower motor
switch is maintained closed by the timing means for a predetermined
time following stopping of the compressor motor by said
electromagnet.
8. The combination recited in claim 6 in which the timing means is
restarted immediately following opening of the compressor motor
switch by the electromagnet, and runs to a predetermined point,
thereby shortening the delay before restart of the compressor
during the time the compressor is stopped by the condition
responsive means.
9. The combination recited in claim 6 in which the blower motor
switch is maintained closed by the timing means until it has run
for a predetermined length of time, and in which the energization
of the electric motor means for the timing means is interrupted in
response to an unfavorable operating condition associated with the
refrigeration system.
Description
BRIEF SUMMARY OF INVENTION
This invention relates to automatic controls and more particularly
to timing devices for controlling and protecting compressors in
refrigeration systems.
The primary object of the invention is the provision of a compact
and simplified control system which stops and starts the
refrigeration compressor at the command of a condition responsive
device and also interposes a delay in restarting the compressor for
protecting against overload.
A further object of the invention is the provision of a simplified
refrigeration control system and control device which provides a
normal delay before restart for pressure equalization following a
normal cycle, but which interposes a substantially longer delay if
the compressor stoppage was due to operation of a safety
control.
Another object of the invention is the provision of a device and
system providing operation of the blower for the refrigeration
system for longer periods than the compressor is operated.
A further object of the invention is to provide a simplified timing
control system using an electric motor, and which operates in a
predetermined cycle without requiring circuitry or switches for
timer motor control.
Another object is to provide a timing device in which operation is
controlled by selectively stalling or releasing the timer
motor.
A further object is to provide a stalling mechanism in which a
timing motor is selectively stalled or released and in which the
actual stalling force is removed from the mechanism controlling the
stalling or releasing.
Other objects will appear from the following description and
appended claims.
BRIEF DESCRIPTION OF DRAWINGS
FIG. 1 is a schematic exploded view of a mechanism embodying the
invention;
FIG. 1a is an enlarged view of the stalling wheel of FIG. 1;
FIG. 2 is a schematic wiring diagram of a complete refrigeration
control system embodying the mechanism of the invention;
FIG. 3 is a chart showing the preferred operating sequence as
occurs on a normal refrigeration cycle;
FIG. 4 is a chart showing a modified operating cycle;
FIG. 5 illustrates a modification of FIG. 1, and in which;
FIG. 6 is a chart showing the operating sequence provided by the
arrangement of FIG. 5.
DETAILED DESCRIPTION OF INVENTION
Referring now to FIG. 1, reference character 1 indicates the timer
motor shown schematically, this motor driving a pinion 2 meshing
with gear 3 which is carried by and drives a shaft 4 which in turn
drives a pinion 5. This pinion drives a final gear 6 which is
carried by and drives a cam shaft 7 carrying a cam 8. The timer
motor 1 drives the final gear 6 and the cam or controller 8 in a
counterclockwise direction as indicated by the arrows.
The timing means above described, through cam 8 operates a
compressor switch generally indicated as 9. This switch or control
device comprises an upper switchblade 10 and a lower switchblade
11, each anchored at its left-hand end and both blades being biased
downwardly toward the cam 8. The lower switchblade 11 is provided
with an opening 12 allowing the blade to straddle the cam 8 and
providing an internal cam follower surface 13. This blade 11
carries a contact 14 and is provided with an extended portion 15
cooperating with the latch 16. The upper switch blade 10 includes a
cam follower bracket 17 which extends downwardly and rides the cam
8 at a point spaced counterclockwise from the cam follower surface
13. Switchblade 10 also carries contact 18 arranged for engaging
contact 14 on switchblade 11. The cam or controller 8 consists of a
main cam surface including a generally circular portion 20 and a
rise portion 21. The cam also includes a dropoff section 22 which
causes dropping of both switchblades with snap action.
The latch 16 is pivoted on a shaft diagrammatically shown as 24 and
includes a latching surface 25 and a camming surface 26, these
surfaces cooperating with extension 15 of lower switchblade 11 as
will be described. The latch 16 also is provided with a biasing
spring 27 which biases this latch toward the end 15 of the
switchblade 11.
The shaft 24 which carries the latch 16 also carries a "run"
stalling lever 30. The latch 16 and the run staller 30 are arranged
to operate in unison. While these two parts are shown as separated
and spaced apart for illustrative purposes, it will be apparent
that these two parts may be molded into a single piece thus
ensuring correct alignment of the working surfaces and lowering
production cost.
The run-stalling member 30 is shown in disengaged position and is
arranged to cooperate with the run-stalling lug 31 carried by the
final gear 6 to provide a mechanical stopping means. When the run
stalling member 30 is rotated counterclockwise, its stalling
surface or movable abutment 32 will be brought into the path of the
stalling lug 31 on the final gear. Thus the final gear will be
stalled when it rotates to the point where lug 31 engages stalling
surface 32. Clockwise rotation of the stalling member 30 takes the
stalling surface 32 out of the path of the stalling lug 31 and thus
the timer is free to proceed beyond this point.
Reference character 35 indicates a solenoid lever which is pivoted
at 36. This lever 35 is biased in a counterclockwise direction by a
spring 37 and is rotated clockwise against the force of spring 37
by the solenoid or electromagnet 38. The solenoid lever 35 includes
an arm 39 carrying a stalling surface 40 adapted to be engaged by a
stalling lug 41 on the final gear 6 providing a mechanical stopping
means. The solenoid lever also carries a pin 42 which is arranged
to engage the switchblade 43 of the blower switch generally
indicated as 44. The switchblade 43 is anchored at its left-hand
end and is biased upwardly. This switchblade includes a movable
contact 45 adapted to engage a stationary contact 46. This
switchblade is biased upwardly for causing the contacts to engage.
The pin 42 on the solenoid lever pushes the switchblade 43
downwardly when the solenoid is deenergized for opening switch
44.
The solenoid lever 35 also carries a pin 50 which is adapted to
engage the portion 51 of the run stall member 30. This pin serves
to rotate the run stall member in a clockwise direction when the
solenoid is deenergized. The solenoid lever is also formed with an
opening 52 through which the supporting shaft 24 for the run stall
member 30 and latch 16 passes. This serves as a stop for limiting
outward travel of the solenoid lever 35 and also limits the inward
travel of the stalling surface 40 on this lever.
The shaft 4 which carries the pinion 5 is journaled in a spring
lever generally indicated as 55. This spring lever is pivotally
supported on the same center as the cam shaft 7 and is biased in a
counterclockwise direction by a spring 56. The amount of
counterclockwise movement is limited by a fixed stop 57. This stop
is located in a manner to cause the gear shaft 4 to be in alignment
with the cam shaft 7 when the spring lever 55 engages stop 57.
Spring lever 55 thus provides a movable bearing for pinion 5. The
pinion 5 is rigidly attached to a stalling wheel 58 having
ratchetlike teeth 59 adapted to come in contact with a stationary
stalling lug 60. The stalling lug 60 may be struckout of the
enclosure for the timing unit or mounted in any suitable manner. It
is preferable that the angle of this lug at the point where engaged
by the stalling wheel be tangent to a circle centered with the
shaft 7. It is also preferable that the teeth of the stalling wheel
be cut so that the stalling surfaces at the point of engagement
with lug 60 are parallel with lug 63. The location of the stalling
lug 60 relative to the fixed stop 57 must be such as to provide
clearance between the stalling wheel 58 and the stalling lug 60
when the spring lever 55 is engaging the fixed stop 57.
FIG. 2 shows the preferred complete refrigeration control system
embodying the mechanism of FIG. 1. This system includes a
compressor motor 70 and a blower motor 71 which blows air across
the evaporator and/or condenser of the refrigeration system. The
compressor motor is controlled by the usual contactor having a
contactor coil C and switches C-1 and C-2 operated thereby. The
system also includes a low-voltage thermostat 72, a low-voltage
transformer 73 and safety controls comprising a high-pressure
cutout 74 and a low-pressure cutout 75. The latter controls and
associated wiring comprise a means for energizing the motor 1. The
operation of the mechanism and complete system will now be
described.
OPERATION OF FIGS. 1 AND 2
With the parts in the positions shown, the system is in the
"Standby" position. The timer solenoid is deenergized which has the
"Standby" stalling surface 40 in the path of lug 41 on final gear
6. Even though the timer motor 1 is energized, no motion can take
place as the timer is effectively stalled. The compressor switch 9
is open and thus the compressor motor contactor C is deenergized
causing the compressor motor to be at rest. Also the blower switch
44 is open and the blower is at rest. Assuming that the pressures
within the refrigeration system are satisfactory and that switches
74 and 75 are closed, the timer motor 1 is energized and is ready
to drive the timer any time the timing mechanism is released by the
stalling mechanism. When the thermostat 72 calls for cooling, it
will energize the timer solenoid 38 which rotates the solenoid
lever 35 about its pivot 36. This closes blower switch 44 and also
removes the stalling surface 40 from the path of the stalling lug
41 on gear 6. This in turn allows the spring 56 to rotate the
spring lever 55 downwardly releasing the stalling wheel 59 from the
stationary stalling lug 60. This same clockwise rotation of
solenoid lever 35 also moves the pin 50 on this lever away from the
surface 51 of the stalling member 30. The stalling member 30
however does not move into stalling position at this time as it is
being held in released position by latch 16.
As the "Standby" stall has been released, the timer motor now
drives the gear 6 and cam 8 in a counterclockwise direction. In a
short time the inclined section 21 of the cam engages the cam
follower surfaces 13 and 17 of the switchblades 10 and 11 and
starts raising the switchblades in unison with the contacts
separated. As lower blade 11 is cammed upwardly, the end 15 rides
up the camming surface 26 on the latch 16 allowing gradual
counterclockwise rotation of the latch. When the end 15 of the
blade rises above the latching surface 25 of the latch, the spring
27 is free to pull the latch into complete latching position. This
same counterclockwise latching motion also causes the run-stalling
member 30 to bring its stalling surface 32 into the path of the
stalling lug 31 on gear 6. Inward travel of the latch 16 and
stalling member 30 is now limited by the surface 51 on member 30
engaging the pin 50 on the solenoid lever 35.
As the cam 8 continues to rotate, the cam follower surface 13 on
switchblade 11 will ride down the dropoff section 22 allowing the
end 15 of the switchblade to rest on the latching surface 25 of
latch 16 which is now in latching position. On continued rotation
of the cam 8, the follower surface 17 on upper switchblade 10 drops
off the dropoff section 22 of the cam. Switchblade 10 now drops
abruptly bringing contact 18 into engagement with contact 14 and
thus closing the load switch 9. This energizes the compressor
contactor coil C which in turn closes its contacts C-1 and C-2
starting the compressor motor 70.
The timing mechanism will now continue to run for a predetermined
time until the run stall lug 31 on gear 6 engages the stalling
surface 32 on the run stall member 30 which is now in stalling
position.
When the run stall member 31 engages the stalling surface 32, it
stops further rotation of the drive gear 6. In reaction to this,
the pinion 5 begins moving bodily in an upward direction, this
motion being allowed by the spring lever 55 disengaging stop 57 and
moving against the bias of the spring 56. When the teeth on the
staller wheel 58 engage the stalling lug 60, the timer motor is
effectively stalled.
Due to the reaction-type stalling mechanism provided by the
invention, the pressure required for stalling at the stalling lugs
31 or 41 is only that required to compress the spring 56
sufficiently to bring the stalling wheel into engagement with the
stalling surface 60. The stalling lugs 31 and 41 on the final gear
are never required to stall the full torque of the motor through
the reduction gears. Instead, the actual stalling force for the
motor is applied ahead of the gear reduction where the torque and
force required is considerably lower. This arrangement in which the
stalling force is merely triggered by the solenoid operated
surfaces makes it possible to design the timer mechanism with the
light duty parts and with a relatively small solenoid. This special
stalling mechanism could be omitted, using a direct drive between
the timer motor and the gear 6. However, this would require the
parts being designed sufficiently strong to carry the relatively
high loads, and to use a solenoid sufficiently strong to engage or
release the higher stalling forces.
On a normal operating cycle, the mechanism will remain in the run
stall position with the switches 9 and 44 closed until the
thermostat 72 is satisfied. When this occurs, it deenergizes the
solenoid 38 causing counterclockwise rotation of the lever 35 by
spring 37. This movement of the solenoid lever 35 causes the pin 50
to engage surface 51 on the stalling member 30 and to rotate this
member clockwise. This simultaneously moves the stalling surface 32
out of the path of the lug 31 and also moves the latch 16 into
released position allowing the switchblade 11 to drop against cam 8
thus opening the compressor switch 9. This same motion of the lever
also causes pin 42 to engage switchblade 43 and thus open the
blower switch 44. Summarizing, opening of the room thermostat
switch 72 deenergizes solenoid 38. This action releases the
run-stop 30 and the latch 16 opening load switch 9 and also opening
the blower switch 44.
The timing mechanism is now free to proceed back to the standby
position where lug 41 on gear 6 engages the standby stalling
surface 40 on solenoid lever 35. It is important on this point of
the cycle that the run lug 31 on the gear 6 be clear of the
stalling surface 40 on the lever 35. This is accomplished by
limiting the inward motion of the stalling surface by a stop as
provided by the edge of hole 52 in lever 35 engaging the shaft 24.
Any other stop arrangement may, of course, be used. The "Run" lug
31 on gear 6 is located inwardly sufficiently that it never engages
the Standby stalling surface 40 even when this surface is in
stalling position. When the lug 41 engages surface 40, the stalling
wheel 58 again engages the stalling lug 60 and stalls the timer
motor 1.
It should be noted that there is only one point in the complete
revolution of the timer cam where the load switch 9 can be closed.
That is the point at which the cam follower surface 17 on switch
blade 10 drops off the dropoff section on the cam. In order to
effect switch closure, the latch 16 must be in place. If the latch
happens to be held released at this time, the load switch will
remain open and it will be necessary for the cam 8 to complete
another complete revolution before the load switch can be
closed.
If during a cycle either the high-pressure switch 74 or
low-pressure switch 75 opens, it will break the circuit to the
transformer 73 thus deenergizing the solenoid 38. This will have
the same effect as dropping out of the solenoid 38 by the
thermostat 72 as described. In other words, it will open the
compressor motor switch stopping the compressor and will also
release the run-stop so that the timer mechanism can proceed back
to the starting point. However, at this time the timer motor is
deenergized as it is in circuit with the switches 74 and 75. Thus
the duration of the unfavorable condition causing opening of the
safety switches is added to the delay in restarting the
compressor.
FIG. 3 shows one type of operating cycle that my control may be
arranged to provide. Here the timer motor speed and gear reduction
are selected to give an overall cycle of one revolution in 7
minutes. The standby lug 41 on gear 6 is located relative to the
dropoff section 22 on cam 8 so as to provide a 20 second delay
between energization of the solenoid 38 and closure of the switch
9. The run stall lug 31 on final gear 6 is located so as to allow a
period of 2 minutes after switch closure before the run lug 31
engages the run-stalling surface on lever 30. This leaves a balance
of 4 minutes 40 seconds that the timer must run before it returns
to the standby position in which lug 41 engages standby stalling
surface 40.
With the cycle as above described, the timer will run for a period
of 2 minutes after the compressor is started. Thus if the
compressor runs the full 2 minutes before stopping, there will be a
delay of 5 minutes before the compressor can be restarted. This is
the sum of the 4 minute 40 second pressure equalization period plus
the 20 second initial delay period.
If the system malfunctions and one of the safety switches 74 or 75
opens, for example 10 seconds after start, the timer must now run
an additional 1 minute 50 seconds before the compressor can be
started. In other words, the timer must now run 6 minutes 50
seconds instead of 5 minutes. In addition, the timer motor is
deenergized during the period that the safety switch remains open
and this indeterminate time is added to the delay imposed by the
timer itself. Thus this system provides substantially longer delays
in event of malfunction than during normal cycle providing only
time enough for pressure equalization.
The 2 minute short cycle adder of course, can be made substantially
longer, even as long as the average on period of the compressor in
the system.
FIG. 4 shows an optional cycle in which the gearing is selected to
provide a 5 minute revolution on the cam shaft. The cam is arranged
to give a 15 second delay in starting and the run lug 31 arranged
to stall the timer immediately after switch 9 closes. This gives a
4 minute 45 second interval for the timer to run to return to the
standby position.
It will be seen that the duration of the short cycle adder can be
made whatever desired simply by selecting the proper gear reduction
and by locating the run-stall lug 31 at the proper angle on gear
6.
FIGS. 5 AND 6
In the embodiment of the invention shown in FIG. 1, the blower
switch 44 is opened and closed by the solenoid 38. If desired, the
blower switch 44 can be held by the timer until a predetermined
period after the compressor is stopped. This arrangement is shown
in FIG. 5 and the operation charted in FIG. 6. Here the pin 42' for
operating switch 44 is carried by a separate lever 80 which is
pivoted on the same bearing 36' as the solenoid lever 35'. The
latch 16 and run stall member 30 are identical with FIG. 1 and are
omitted from FIG. 5 for reasons of clarity. The lever 80 is biased
counterclockwise by a spring 81 and carries a standby-stalling
surface 82 adapted to be engaged by a stalling surface 83 carried
on a cam 84 located between the cam 8 and the final gear 6'. A pin
85 carried by the solenoid lever 35' is arranged to engage a
surface 86 on the lever 80, this pin causing clockwise rotation of
the lever 80 when the lever 35' is rotated in the same direction by
energization of the solenoid.
In operation, energization of the solenoid rotates the lever 35'
clockwise which lifts the lever 80 releasing the pin 42' from
switch 44 and also releasing the stalling surface 82 from the
corresponding surface 83 on cam 84. The cam 84 will now hold lever
80 in this position until the timer rotates to the point where the
dropoff portion 87 on the cam clears the cam follower surface of
lever 80. At this time, the spring 81 is free to rotate the lever
80 clockwise opening switch 44 and also bringing the stalling
surface 82 into position for stalling cam 84.
The arrangement shown in FIG. 5 has the advantage of maintaining
the blower in operation in the event that the compressor is shut
down by either safety switch 74 or 75. Operation of the blower at
this time helps to remove the condition causing the shut down.
From the foregoing, it will be apparent that the invention provides
an extremely simple compressor control system. Only one switch is
required to give response to the thermostat and to provide starting
of the compressor or load. In addition, the invention provides for
control of the blower giving blower operation both before and after
the compressor running cycle. In addition, the invention provides
for extra delay in the event of short cycle, thus giving additional
protection to the compressor. It will also be apparent that
substantial changes in the operating cycle may be made as desired,
simply by selecting the necessary gear reduction and locating the
stall lugs at the proper locations on the final gear.
While a preferred form of the invention has been shown and
described, many changes may be made without departing from the
spirit and scope of the invention as defined in the following
claims.
* * * * *