U.S. patent application number 16/132166 was filed with the patent office on 2019-01-17 for high-efficiency extra-large cooling capacity series chiller in energy station.
The applicant listed for this patent is JIANGSU QUYU ENERGY CO., LTD.. Invention is credited to Pengyue JI, Junwu LU, Bin PAN, Hao SUN, Ting ZHAN, Zhenfeng ZHU.
Application Number | 20190017712 16/132166 |
Document ID | / |
Family ID | 63352195 |
Filed Date | 2019-01-17 |
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United States Patent
Application |
20190017712 |
Kind Code |
A1 |
ZHAN; Ting ; et al. |
January 17, 2019 |
HIGH-EFFICIENCY EXTRA-LARGE COOLING CAPACITY SERIES CHILLER IN
ENERGY STATION
Abstract
A high-efficiency extra-large cooling capacity series
water-cooled chiller in an energy station, comprising at least two
evaporators, a condenser, a chilled water main pipe and a cooling
water main pipe, all the evaporators form an evaporator series set
in a series connection form, both ends of the evaporator series set
are connected to the chilled water main pipe, and each evaporator
is provided with a refrigerant channel for connecting the
condenser. According to the present invention, the evaporators are
set in series combination. When the load is very low, one
compressor operates at a high load or at full load, that is, the
compressor continuously operates in a high efficiency zone, which
avoids multiple compressors operating in an inefficient zone, and
high total power.
Inventors: |
ZHAN; Ting; (Yixing, CN)
; SUN; Hao; (Yixing, CN) ; JI; Pengyue;
(Yixing, CN) ; LU; Junwu; (Yixing, CN) ;
ZHU; Zhenfeng; (Yixing, CN) ; PAN; Bin;
(Yixing, CN) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
JIANGSU QUYU ENERGY CO., LTD. |
Yixing |
|
CN |
|
|
Family ID: |
63352195 |
Appl. No.: |
16/132166 |
Filed: |
September 14, 2018 |
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F25B 5/04 20130101; F24F
3/06 20130101; F24F 3/08 20130101; F25B 2339/047 20130101; F25B
2400/06 20130101; F25B 2339/0242 20130101; F25B 25/005 20130101;
F25B 2700/21173 20130101; F24F 3/065 20130101 |
International
Class: |
F24F 3/06 20060101
F24F003/06; F25B 5/04 20060101 F25B005/04; F25B 25/00 20060101
F25B025/00; F24F 3/08 20060101 F24F003/08 |
Foreign Application Data
Date |
Code |
Application Number |
May 23, 2018 |
CN |
201810500187X |
Claims
1. A high-efficiency extra-large cooling capacity series chiller in
an energy station, comprising at least two evaporators (1), a
condenser (3), a chilled water main pipe (21) and a cooling water
main pipe (31), wherein all the evaporators (1) form an evaporator
series set in a series connection form, both ends of the evaporator
series set are connected to the chilled water main pipe (21), and
each evaporator (1) is provided with a refrigerant channel (5) for
connecting the condenser (3), the refrigerant channel (5) is
divided into two parts comprising a refrigerant supply channel (51)
and a refrigerant return channel (52), the refrigerant supply
channel (51) and the refrigerant return channel (52) are
respectively provided with a relief valve (4) and the compressor
(2), the evaporator (1) is internally provided with a temperature
sensor (10) for collecting a temperature of chilled water leaving
the evaporator (1), and the temperature sensor (10) is connected to
the corresponding compressor (2).
2. The high-efficiency extra-large cooling capacity series
water-cooled chiller in an energy station according to claim 1,
wherein the evaporator series set is embedded in the chilled water
main pipe (21).
3. The high-efficiency extra-large cooling capacity series chiller
in an energy station according to claim 1, wherein an evaporating
shell pass (11) of the evaporator (1) serves as a refrigerant
channel, and the evaporator (1) is internally provided with a
plurality of evaporating tube passes (12) as chilled water
channels.
4. The high-efficiency extra-large cooling capacity series chiller
in an energy station according to claim 1, wherein the condenser
(3) is embedded in the cooling water main pipe (31), a condensing
shell pass (32) of the condenser (3) serves as a refrigerant
channel, and the condenser (3) is internally provided with a
plurality of condensing tube passes (33) as cooling water
channels.
5. The high-efficiency extra-large cooling capacity series chiller
in an energy station according to claim 1, wherein a total length
of the refrigerant channel (5) is no more than 200 meters.
6. The high-efficiency extra-large cooling capacity series chiller
in an energy station according to claim 1, wherein the condenser
(3) is placed on the ground and the evaporator (1) is suspended
above the condenser (3).
7. The high-efficiency extra-large cooling capacity series chiller
in an energy station according to claim 1, wherein the evaporator
(1) and the chilled water main pipe (21) are connected by a
reduction nipple.
8. The high-efficiency extra-large cooling capacity series chiller
in an energy station according to claim 3, wherein a total
cross-sectional area of the evaporating tube passes (12) is no less
than a cross-sectional area of the chilled water main pipe
(21).
9. The high-efficiency extra-large cooling capacity series chiller
in an energy station according to claim 4, wherein a total
cross-sectional area of the condensing tube passes (33) is no less
than a cross-sectional area of the cooling water main pipe
(31).
10. The high-efficiency extra-large cooling capacity series chiller
in an energy station according to claim 2, wherein the condenser
(3) is placed on the ground and the evaporator (1) is suspended
above the condenser (3).
11. The high-efficiency extra-large cooling capacity series chiller
in an energy station according to claim 3, wherein the condenser
(3) is placed on the ground and the evaporator (1) is suspended
above the condenser (3).
12. The high-efficiency extra-large cooling capacity series chiller
in an energy station according to claim 4, wherein the condenser
(3) is placed on the ground and the evaporator (1) is suspended
above the condenser (3).
13. The high-efficiency extra-large cooling capacity series chiller
in an energy station according to claim 5, wherein the condenser
(3) is placed on the ground and the evaporator (1) is suspended
above the condenser (3).
Description
[0001] This application claims priority to Chinese Patent
Application Ser. No. CN 201810500187X filed on May 23, 2018.
TECHNICAL FIELD
[0002] The present invention relates to a water-cooled chiller, and
more particularly, to a high-efficiency extra-large cooling
capacity series water-cooled chiller in an energy station using a
multistage pipe embedded evaporator.
BACKGROUND
[0003] Present water-cooled chillers, compressors, evaporators,
condensers and expansion valves are compactly assembled together.
When multiple chillers are used in parallel, chilled water with
higher temperature flew back at the tail end of the chiller will
enter each parallel chiller along branches of chilled water return
main pipes. After being cooled, the chilled water will be
incorporated to the chilled water main supply pipes through each
chilled water supply branch, and then supplied to the tail end.
This type of chiller takes up a lot of space because of the
connection of multiple branches and the reasonable installation
space required by the chiller itself.
[0004] The chiller operates at high load rates with high efficiency
and operates at low and medium loads with low efficiency. When the
tail end load is small, that is, the cooling demand is small, but
the chilled water flow demand is large because the cooling area is
large, a single chiller can operate in the high efficiency zone
when the existing chiller is used in the case that the number of
operating chillers is small. The total power is lower, but due to
the limitation of the pipe diameter of the evaporator, the flow of
the chilled water delivered is small, such that there is
insufficient chilled water flow at the tail end, and the cooling
effect is poor in some areas. If the number of operating chillers
is large, the chilled water delivered can meet the tail end demand,
but a single chiller operates in a low-load, low-efficiency zone,
which has a high total power. Because the chillers are selected
according to the highest cooling load, the chillers operate under
the above-mentioned low-load conditions in most of the time, and
the energy consumption of a cold water host is high.
[0005] In order to ensure the safe operation of the chiller, no
matter the chiller operates in high or low and medium loads, the
chilled water pump must continue to provide a basic fixed head
consumption for the chiller, generally no less than 80 kPa,
resulting in high energy consumption of the chilled water pump.
[0006] The designed chilled water supply and return temperature
difference of the existing chiller is generally 5 to 8.quadrature..
When the actual temperature difference is higher or lower than the
design value during operation, the efficiency of the chiller will
decrease. In addition, the existing chillers cannot achieve a given
chilled water return temperature by adjusting the chilled water
supply temperature (6 to 12.quadrature.) in a wide range.
Therefore, for the project which requires frequently changed
temperature difference at the tail end and can keep comfortable at
a fixed return temperature, the existing chiller cannot provide the
cooling capacity continuously, efficiently and effectively.
SUMMARY
[0007] Object of the present invention: in order to overcome the
deficiencies in the prior art, a high-efficiency extra-large
cooling capacity series water-cooled chiller in an energy station
with high operating efficiency and small energy consumption and
using a multistage pipe embedded evaporator is provided.
[0008] Technical solutions: in order to achieve the above object,
the present invention provides a high-efficiency extra-large
cooling capacity series water-cooled chiller in an energy station
comprising at least two evaporators, a condenser, a chilled water
main pipe and a cooling water main pipe. All the evaporators form
an evaporator series set in a series connection form, both ends of
the evaporator series set are connected to the chilled water main
pipe, and each evaporator is provided with a refrigerant channel
for connecting the condenser, the refrigerant channel is divided
into two parts comprising a refrigerant supply channel and a
refrigerant return channel, the refrigerant supply channel and the
refrigerant return channel are respectively provided with a relief
valve and the compressor, the evaporator is internally provided
with a temperature sensor for collecting a temperature of chilled
water leaving the evaporator, and the temperature sensor is
connected to the corresponding compressor.
[0009] The design principle of the present invention is as follows:
the evaporators are arranged in series combination, and each
evaporator can reduce the temperature of the chilled water by about
3 degrees at the rated flow rate and the full load of the
compressor. When the load is very low, one compressor operates at a
high load or at full load, that is, the compressor continuously
operates in a high efficiency zone, which avoids multiple
compressors being operated in an inefficient zone, and high total
power, so that the energy consumption of the chiller is greatly
saved. Moreover, because the series structure is adopted, one
evaporator operation can provide the same chilled water flow as
that of three evaporator operation, which can meet the chilled
water flow demand at the tail end.
[0010] Further, the evaporator series set is embedded in the
chilled water main pipe.
[0011] Further, an evaporating shell pass of the evaporator serves
as a refrigerant channel, and the evaporator is internally provided
with a plurality of evaporating tube passes as chilled water
channels. The evaporating tube pass is a single-pass structure, a
water pressure drop of each evaporator is 6 to 8 kPa, and the water
pressure drop is 18 to 24 kPa if three evaporators are connected in
series, which is obviously smaller than a water pressure drop (50
to 100 kPa) of an evaporator of the current chiller, so that an
energy consumption of a chilled water pump can be reduced.
[0012] Further, the condenser is embedded in the cooling water main
pipe, a condensing shell pass of the condenser serves as a
refrigerant channel and the condenser is internally provided with a
plurality of condensing tube passes as cooling water channels, such
that both the refrigerant and the cooling water have respectively
independent channels and will not contact and interfere with each
other. The refrigerant flows between the separate evaporators and
the overall condenser. No matter how many evaporators are
operating, the refrigerant can maximize the heat exchange area in
the condenser and improve the operating efficiency of each
compressor.
[0013] Further, a total length of the refrigerant channel is no
more than 200 meters, and a length of the refrigerant channel
should not be too long, which may affect the using effect of the
refrigerant.
[0014] Further, the condenser is placed on the ground, and the
evaporator is suspended above the condenser. The evaporator does
not occupy the floor space, which can reduce an area of a central
air-conditioning room.
[0015] Further, the evaporator and the chilled water main pipe are
connected by a reduction nipple, so that the evaporators of
different pipe diameters can be perfectly jointed with the chilled
water main pipe.
[0016] Further, a total cross-sectional area of the condensing tube
passes is no less than a cross-sectional area of the chilled water
main pipe, and a total cross-sectional area of the condensing tube
passes is no less than a cross-sectional area of the cooling water
main pipe, thus reducing the resistance for the chilled water and
the cooling to flow in and out of the evaporator and the condenser
respectively, and making the chilled water and the cooling water
flow in and out more smoothly.
[0017] Beneficial effects: compared with the prior art, the present
invention has the following advantages.
[0018] 1. The evaporators are set in series combination. When the
load is very low, one compressor operates at a high load or at full
load, that is, the compressor continuously operates in a high
efficiency zone, which avoids multiple compressors being operated
in an inefficient zone, and high total power, so that the energy
consumption of the chiller is greatly saved.
[0019] 2. Both the tube passes and the shell passes are single-pass
structures, so that the chilled water and the cooling water do not
require a return stroke. Compared with the original return
structure, the flow resistance of the chilled water and the cooling
water is reduced, thereby reducing the energy consumption.
[0020] 3. Because of the series structure, one evaporator operation
can provide the same chilled water flow as that of multiple
evaporator operation, which can meet the chilled water flow demand
at the tail end, so that each compressor can meet the chilled water
demand at the tail end on the basis of keeping high efficiency
operating, which not only guarantees the cooling effect, but also
greatly saves the energy consumption and reduces the operating
costs, thus being very suitable for large-area centralized
cooling.
BRIEF DESCRIPTION OF THE DRAWINGS
[0021] FIG. 1 is a structural schematic diagram of the present
invention;
[0022] FIG. 2 is a sectional drawing of an evaporator;
[0023] FIG. 3 is a sectional drawing of a condenser;
[0024] FIG. 4 is a structural schematic diagram of a chiller in a
second embodiment; and
[0025] FIG. 5 is a partial schematic diagram of a flow direction of
cooling water.
DETAILED DESCRIPTION
[0026] The invention will be further clarified with reference to
the accompanying drawings and specific embodiments. It should be
appreciated that these embodiments are intended to illustrate the
invention and not to limit the scope of the invention.
Modifications of equivalent forms to the invention made by those
skilled in the art after reading the invention all fall within the
scope defined by the appended claims of the application.
First Embodiment
[0027] As shown in FIG. 1 to FIG. 3, the present invention provides
a high-efficiency extra-large cooling capacity series water-cooled
chiller in an energy station comprising three evaporators 1, a
condenser 3, a chilled water main pipe 21 and a cooling water main
pipe 31. The three evaporators 1 are embedded in the chilled water
main pipe 21, each evaporator 1 is provided with a refrigerant
channel 5 for connecting the condenser 3, each refrigerant channel
5 is divided into two parts comprising a refrigerant supply channel
51 and a refrigerant return channel 52, the refrigerant supply
channel 51 and the refrigerant return channel 52 are respectively
provided with a relief valve 4 and the compressor 2, the evaporator
1 is internally provided with a temperature sensor 10 for
collecting a temperature of chilled water leaving the evaporator 1,
and the temperature sensor 10 is connected to the corresponding
compressor 2. The evaporator 1 adopts a structure of a full liquid
evaporator, an evaporating shell pass 11 of the evaporator 1 serves
as a refrigerant channel, and the evaporator 1 is internally
provided with a plurality of evaporating tube passes 12 as chilled
water channels, and the condenser 3 is embedded in the cooling
water main pipe 31. The condenser 3 adopts a structure of a full
liquid condenser, a condensing shell pass 32 of the condenser 3
serves as a refrigerant channel, and the condenser 3 is internally
provided with a plurality of condensing tube passes 33 as cooling
water channels, and a total length of the refrigerant channel 5 is
100 meters. The condenser 3 is placed on the ground and the
evaporator 1 is suspended above the condenser 3. Both the
evaporator 1 and the chilled water main pipe 21, and the condenser
3 and the cooling water main pipe 31 are connected by a reduction
nipple. A total cross-sectional area of the evaporating tube passes
12 is no less than a cross-sectional area of the chilled water main
pipe 21, and a total cross-sectional area of the condensing tube
passes 33 is no less than a cross-sectional area of the cooling
water main pipe 31.
Second Embodiment
[0028] A target temperature value of a chilled water supply
temperature of the chiller was preset. As shown in FIGS. 2 and 4,
three evaporators 1 were respectively recorded as an evaporator a,
an evaporator b and an evaporator c, and chilled water return water
6 entered an evaporating tube pass 12 of the evaporator a through a
chilled water main pipe 21, a refrigerant was located in an
evaporating shell pass 11 of the evaporator a, and the refrigerant
exchanged heat with the chilled water return water 6 in the
evaporating tube pass 12 to become a gaseous state, the temperature
of the chilled water return water 6 dropped, a relief valve 4a was
opened, the gaseous refrigerant entered a refrigerant supply
channel 51a, and then flowed into a condenser 3. The gaseous
refrigerant flew in a condensing shell pass 32 of the condenser 3,
and the gaseous refrigerant was turned into a liquid state by the
compression of a compressor 2a and returned to the evaporator a
through a refrigerant circuit channel 52a. The process was
circulated in this way.
[0029] Therefore, when the compressor 2a and the condenser 3 were
operating, the refrigerant flew between the evaporator 1 and the
entire condenser 3, completing the process of transferring heat
from the evaporator 1 to the condenser 3, and the temperature of
the chilled water dropped. A temperature sensor 10a collected a
temperature value of the chilled water leaving the evaporator a as
the operation basis for a compressor 2b. When the temperature value
collected by the temperature sensor 10a was higher than the preset
target temperature value, the temperature sensor 10a sent a start
instruction to the compressor 2b.
[0030] The chilled water return water 6 entered the evaporator b, a
relief valve 4b was in an opened state. The gaseous refrigerant
entered a refrigerant supply channel 51b, and then flew into the
condenser 3. The gaseous refrigerant flew in the condensing shell
pass 32 of the condenser 3, and the gaseous refrigerant was turned
into a liquid state by the compression of a compressor 2b and
returned to the evaporator b through a refrigerant return channel
52b. The process was circulated in this way.
[0031] Therefore, when the compressor 2b and the condenser 3 were
operating, the refrigerant flew between the evaporator 1 and the
entire condenser 3, completing the process of transferring heat
from the evaporator 1 to the condenser 3, and the temperature of
the chilled water dropped again. A temperature sensor 10b collected
a temperature value of the chilled water leaving the evaporator b
as the operation basis for a compressor 2c. When the temperature
value collected by the temperature sensor 10b was higher than the
preset target temperature value, the temperature sensor 10b sent a
start instruction to the compressor 2c.
[0032] The chilled water return water 6 entered the evaporator c, a
relief valve 4c was in an opened state. The gaseous refrigerant
entered a refrigerant supply channel 51c, and then flew into the
condenser 3. The gaseous refrigerant flew in the condensing shell
pass 32 of the condenser 3, and the gaseous refrigerant was turned
into a liquid state by a compressor 2c and returned to the
evaporator c through a refrigerant return channel 52c. When the
compressor 2c and the condenser 3 were operating, the refrigerant
flew between the evaporator 1 and the entire condenser 3,
completing the process of transferring heat from the evaporator 1
to the condenser 3, and the temperature of the chilled water
dropped again. A temperature sensor 10c collected a temperature
value of the chilled water leaving the evaporator c, and the
chilled water was outputted through the chilled water main pipe 21
as chilled water supply water 7.
Third Embodiment
[0033] A target temperature value of a chilled water supply
temperature of the chiller was preset. As shown in FIGS. 2 and 4,
three evaporators 1 were respectively recorded as an evaporator a,
an evaporator b and an evaporator c, and chilled water return water
6 entered an evaporating tube pass 12 of the evaporator a through a
chilled water main pipe 21, a refrigerant was located in an
evaporating shell pass 11 of the evaporator a, and the refrigerant
exchanged heat with the chilled water return water 6 in the
evaporating tube pass 12 to become a gaseous state, the temperature
of the chilled water return water 6 dropped, a relief valve 4a was
in opened state, the gaseous refrigerant entered a refrigerant
supply channel 51a, and then flowed into a condenser 3. The gaseous
refrigerant flew in a condensing shell pass 32 of the condenser 3,
and the gaseous refrigerant was turned into a liquid state by a
compressor 2a and returned to the evaporator a through a
refrigerant return channel 52a. When the compressor 2a and the
condenser 3 were operating, the refrigerant flew between the
evaporator 1 and the entire condenser 3, completing the process of
transferring heat from the evaporator 1 to the condenser 3, and the
temperature of the chilled water dropped. A temperature sensor 10a
collected a temperature value of the chilled water leaving the
evaporator a as the operation basis for a compressor 2b; when the
temperature value collected by the temperature sensor 10a was lower
than the preset target temperature value, a relief valve 4b, a
relief valve 4c, the compressor 2b and a compressor 2c were all in
a closed and stopped state, which did not cool the chilled water
return water 6. The chilled water return water 6 passed through the
evaporator b and the evaporator c in sequence, and was finally
outputted through the chilled water main pipe 21 as chilled water
supply water 7.
Fourth Embodiment
[0034] As shown in FIG. 1 and FIG. 5, a condenser 3 was connected
to a cooling water main pipe 31, and was powered by a cooling pump.
Cooling water return water 8 cooled by a cooling tower entered the
condenser 3 to cool the condenser 3, and take away the heat of the
condenser 3. Cooling water effluent 9 flew to the cooling tower 91,
and the process was circulated in this way.
[0035] It can be known from the second embodiment and the second
embodiment that no matter how many compressors 2 are compressor,
each compressor 2 can maintain full load operation, avoiding the
compressor 2 in a low load operating state. The operating
efficiency of the chiller is very efficient, and the energy
consumption is reduced.
* * * * *