CN211120563U - Multi-stage compression multi-condenser intermediate complete cooling heat pump drying system - Google Patents
Multi-stage compression multi-condenser intermediate complete cooling heat pump drying system Download PDFInfo
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- CN211120563U CN211120563U CN201921465776.5U CN201921465776U CN211120563U CN 211120563 U CN211120563 U CN 211120563U CN 201921465776 U CN201921465776 U CN 201921465776U CN 211120563 U CN211120563 U CN 211120563U
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Abstract
The utility model discloses a complete cooling heat pump drying system in middle of many condensers of multistage compression. The utility model consists of an evaporator, an air cooler, compressors at all levels, condensers at all levels, throttle valves at all levels and gas coolers at all levels, wherein the ith gas cooler is connected with the ith condenser which is connected with the ith compressor; the ith stage gas cooler is connected with the (i + 1) th stage compressor, the (i + 1) th stage compressor is connected with the (i + 1) th stage gas cooler, the (i + 1) th stage gas cooler is connected with the (i + 1) th stage condenser, the (i + 1) th stage condenser is connected with the (i + 1) th stage throttling valve, and the (i + 1) th stage throttling valve is connected with the (i) th stage throttling valve. Through the multi-stage compression and multi-stage variable temperature condensation processes of the working medium, the air is continuously heated for many times, and the irreversible loss of heat exchange with the working medium in the air heating process can be obviously reduced.
Description
Technical Field
The utility model relates to a heat pump technology field especially relates to a complete cooling heat pump drying system in middle of multi-stage compression multi-condenser.
Background
Drying is a widely used process in the production and processing of agricultural products. The proportion of drying to industrial energy consumption is higher, and energy can be saved by adopting the heat pump technology to dry agricultural products. At present, the heat pump drying technology is widely applied to the fields of wood, tobacco, food and vegetable dehydration and the like. Further improving the energy efficiency of the heat pump drying equipment has important practical significance and social value for promoting energy conservation and emission reduction and improving economic benefits.
The conventional heat pump drying system is adopted, the condensing temperature is constant, air is directly heated in the condenser, the temperature difference between the inlet and the outlet of the air is large and is limited by the heat exchange temperature difference between the working medium of the condenser and the air, the heat exchange temperature difference distribution of fluid on two sides in the condenser is seriously uneven, the average heat exchange temperature difference in the condenser is large, the heat exchange process generates large irreversible loss, and the system energy efficiency is low. The conventional single-stage compression heat pump system using the non-azeotropic working medium has the advantages that the temperature slippage in the evaporation and condensation processes is equivalent, and the system is suitable for the working condition that the temperature change of heat exchange fluid at the heat source side and the heat sink side is close to each other. And for the working condition that the temperature of the heat source and the heat sink spans a large range, the conventional compressor has large compression ratio and low efficiency.
SUMMERY OF THE UTILITY MODEL
The utility model provides an adopt multistage compression multistage condensation heat pump drying system to it is big, the compression ratio is big to solve the irreversible loss of heat transfer process, and the problem that the system efficiency is low.
The utility model discloses a complete cooling heat pump drying system in the middle of a multi-stage compression multi-condenser, i is more than or equal to 3 and less than or equal to n-1 in the system, n is more than or equal to 4;
the outlet of the first-stage compressor 3 is connected with the working medium side inlet of the first-stage gas cooler 4, the working medium side outlet of the first-stage gas cooler 4 is connected with the working medium side inlet of the first-stage condenser 5, the working medium side outlet of the first-stage condenser 5 is connected with the inlet of the first-stage throttle valve 6, the outlet of the first-stage throttle valve 6 is connected with the working medium side inlet of the evaporator 2, and the working medium side outlet of the evaporator 2 is connected with the inlet of the first-stage compressor 3; the working medium side outlet of the first stage gas cooler 4 is connected with the inlet of the second stage compressor 7, the outlet of the second stage compressor 7 is connected with the working medium side inlet of the second stage gas cooler 8, the working medium side outlet of the second stage gas cooler 8 is connected with the inlet of the second stage condenser 9, the outlet of the second stage condenser 9 is connected with the inlet of the second stage throttle valve 10, and the outlet of the second stage throttle valve 10 is connected with the inlet of the first stage throttle valve 6;
an outlet at the working medium side of the ith stage gas cooler 11 is connected with an inlet of an ith stage condenser 12, and an outlet of the ith stage condenser 12 is connected with an inlet of an ith stage compressor; the working medium side outlet of the ith stage gas cooler 11 is connected with the inlet of an i +1 th stage compressor 14, the outlet of the i +1 th stage compressor 14 is connected with the working medium side inlet of an i +1 th stage gas cooler 15, the working medium side outlet of the i +1 th stage gas cooler 15 is connected with the inlet of an i +1 th stage condenser 16, the outlet of the i +1 th stage condenser 16 is connected with the inlet of an i +1 th stage throttle valve 17, and the outlet of the i +1 th stage throttle valve 17 is connected with the inlet of an i +1 th stage throttle valve 13;
the outlet of the n-1 stage compressor is connected with the working medium side inlet of the n-1 stage gas cooler 18, the working medium side outlet of the n-1 stage gas cooler 18 is connected with the inlet of the n-1 stage condenser 19, the outlet of the n-1 stage condenser 19 is connected with the inlet of the n-1 stage throttle valve 20, and the working medium side outlet of the n-1 stage throttle valve 20 is connected with the inlet of the n-2 stage throttle valve; the working medium side outlet of the n-1 stage gas cooler 18 is connected with the inlet of the nth stage compressor 21, and the outlet of the nth stage compressor 21 is connected with the working medium side inlet of the nth stage condenser 22; the working medium side outlet of the nth-stage condenser 22 is connected with the inlet of an nth-stage throttle valve 23, and the outlet of the nth-stage throttle valve 23 is connected with the inlet of an n-1 st-stage throttle valve 20;
the outlet of the drying chamber 25 is connected to the air-side inlet of the air cooler 24, the air-side outlet of the air cooler 24 is connected to the air-side inlet of the evaporator 2, the air-side outlet of the evaporator 2 is connected to the air-side inlet of the first stage condenser 5, the air-side outlet of the first stage condenser 5 is connected to the air-side inlet of the first stage gas cooler 4, the air-side outlet of the first stage gas cooler 4 is connected to the air-side inlet of the second stage condenser 9, the air-side outlet of the second stage condenser 9 is connected to the air-side inlet of the second stage gas cooler 8, the air-side outlet of the second stage gas cooler 8 is connected to the air-side inlet of the third stage condenser, the air-side outlet of the third stage condenser is connected to the air-side inlet of the third stage gas cooler, the air-side outlet of the n-1 stage gas cooler 18 is connected to the air-side inlet of the n-stage condenser 22.
The working medium can be pure refrigerant such as R1234ze (Z), R1234ze (E), R1233zd (E), R1224yd (Z), R1336mzz (Z), R365mfc, R1234yf and R245fa, and can also be CO2/R1234ze(E)、 CO2/R1234ze(Z)、CO2Non-azeotropic mixed working media such as/R1234 yf, R41/R1234ze (E), R41/R1234ze (Z), R41/R1234yf, R32/R1234ze (E), R32/R1234ze (Z), R32/R1234yf and the like. For non-azeotropic mixed working medium, the refrigerant with temperature slippage equivalent to the temperature difference of the heat exchange fluid inlet and outlet of the evaporator is selected.
The grade number determination principle is as follows: in order to ensure that the heat exchange processes of the evaporator and the condenser are matched simultaneously, the temperature rise of the normal-temperature water heating and the temperature drop of the heat source heat exchange fluid are calculated according to the process requirements (the normal-temperature water heating temperature rise/the heat source heat exchange fluid cooling temperature drop), and the whole is taken as the series number of the system.
The utility model discloses the system can also be with each temperature level condenser and the parallelly connected heating hot water heating pipeline of each temperature level gas cooler, the application is the complete cooling heat pump two ally oneself with confession system in the middle of the multi-stage compression multi-condenser. The heat supply end can be connected with devices such as a fan coil, a ground coil and a radiator, and condensers and gas coolers at all levels directly supply heat for the devices, so that the heat is supplied to rooms, the gradient utilization of heat is realized, and the loss of heat is reduced.
Compared with the prior art, the utility model has the advantages and positive effect be:
(1) compared with the conventional pure single-stage compression heat pump system, the air is continuously heated in the multistage condensers, the temperature rise of the air in each condenser is lower, the condensing process of each temperature position of the working medium and the air heating process form good temperature matching, the heat exchange temperature difference between the air and the working medium can be obviously reduced, the irreversible loss of heat exchange between the air and the working medium is reduced,
the efficiency is improved, and the COP of the circulation is effectively improved;
(2) for a conventional single-stage compression heat pump system adopting a non-azeotropic working medium, the working medium in an evaporator and a condenser is difficult to meet the requirement of simultaneous matching with the air temperature. Compare with conventional non-azeotropic medium single-stage compression heat pump system, the utility model discloses the heating process of humid air is through twice and the continuous intensification more than twice, and the temperature rise of heating process at every turn is not high, and the condensation process with non-azeotropic refrigerant evaporation process and each temperature position forms fine temperature and matches. Through the utility model discloses, can realize that evaporimeter and condenser both sides fluid match simultaneously, the irreversible loss of heat transfer reduces greatly, further improves the system
The efficiency and the energy efficiency are improved, and the economic benefit is improved;
(3) the more the second stage of the compressor is less in gas transmission amount, the lower the suction amount of the compressor is, and compared with a single-stage heat pump system under the same air temperature rise condition, the size of the compressor is reduced, and the power consumption is obviously reduced;
(4) compared with the traditional single-stage compression, the pressure ratio in the multi-stage compression process is reduced, the isentropic efficiency of the compressor is improved, in addition, the device of the utility model is provided with a gas cooler for cooling the outlet of the compressor, the exhaust temperature is reduced, and the service life of the compressor is prolonged;
drawings
FIG. 1 is a diagram of a dual stage compression dual condenser intercooled full cool heat pump drying system;
FIG. 2 is a temperature-enthalpy diagram of a single-stage pure conventional heat pump drying system;
FIG. 3 is a temperature-enthalpy diagram of a drying system of a dual-stage pure compression heat pump with dual condensers for intermediate complete cooling of the heat pump;
FIG. 4 is a temperature-enthalpy diagram of a drying system of a double-stage non-azeotropic working medium compression heat pump and double condensers with intermediate complete cooling of the heat pump;
fig. 5 is a diagram of a multi-stage compression multi-condenser intermediate complete heat pump drying system.
Detailed Description
The present invention will be further explained with reference to the accompanying drawings.
The first embodiment is as follows: double-stage compression double-condenser intermediate complete cooling heat pump drying system
The system consists of a first-stage heat pump cycle and a second-stage heat pump cycle and a process that wet air in a drying chamber is continuously heated, and the system is shown in figure 1.
(1) If the system adopts pure working medium, the temperature-enthalpy diagram of the single-stage pure conventional heat pump drying system is shown in figure 2.
The specific implementation mode is as follows:
the first step is as follows: the first stage compressor 3 sucks the low-temperature and low-pressure working medium (as shown in state "1" of fig. 2) at the working medium side outlet of the evaporator 2, and compresses the working medium into medium-temperature and medium-pressure superheated gas (as shown in state "2" of fig. 2). Then the hot gas flows into the working medium side inlet of the first stage gas cooler 4, and the temperature of the working medium in the first stage gas cooler 4 is reduced after heat exchange (as shown in the state 3 in figure 2). Then the gas flows into a first-stage condenser 5 to be condensed to saturated liquid (as shown in a state 4 of figure 2), then the working medium enters a first-stage throttle valve 6 to be throttled and depressurized to a two-phase fluid state (as shown in a state 5 of figure 2), the gas-liquid two-phase fluid enters a working medium side inlet of an evaporator 2, the working medium is changed into a saturated gas state (as shown in a state 1 of figure 2) after evaporating and absorbing the heat of the air, and the heat pump circulation is completed.
The second step is that: the wet air (as shown in state a3 of fig. 2) flowing out of the drying chamber 25 and performing heat and moisture exchange with the material flows into the air cooler 24 to release a part of sensible heat, so that the temperature of the wet air is initially reduced to state a2 of fig. 2, then flows into the evaporator 2, the temperature and the humidity are simultaneously reduced, at this time, the air is in a state of lower temperature and lower humidity (as shown in state a1 of fig. 2), then the air flows into the first-stage condenser 5 to be heated to state a4 of fig. 2, and enters the drying chamber after being heated to a higher temperature, and after performing heat and moisture exchange with the material (as shown in state a3 of fig. 2), the air flows into the air cooler 24 to be cooled to state a2 of fig. 2, and the air side.
(2) If the system adopts pure working medium, the temperature-enthalpy diagram of the drying system of the heat pump with double-stage pure compression and double-condenser intermediate complete cooling is shown in figure 3. The specific implementation mode is as follows:
the first step is as follows: the first-stage compressor 3 sucks a low-temperature and low-pressure working medium (as shown in a state 1 in a figure 3) at an outlet at a working medium side of the evaporator 2, the working medium is compressed into medium-temperature and medium-pressure superheated gas (as shown in a state 2 in a figure 3), the superheated gas flows into a working medium side inlet of the first-stage gas cooler 4, the temperature of the working medium in the first-stage gas cooler 4 is reduced after heat exchange (as shown in a state 3 in a figure 3), the gas is divided into two paths, one path of the gas flows into the first-stage condenser 5 to be condensed into saturated liquid (as shown in a state 8 in a figure 3), the working medium enters the first-stage throttle valve 6 to be throttled and reduced to a two-phase fluid state (as shown in a state 11 in a figure 3), the gas-liquid two-phase fluid enters the working medium side inlet.
The second step is that: the other superheated gas from the first stage gas cooler 4 flows into the second stage compressor 7, compressed into high temperature and high pressure fluid (as shown in state "4" of fig. 3), and then flows into the second stage condenser 9, and exchanges heat with the air flowing out of the first stage condenser (as shown in states a6 and a4 of fig. 3, and a6 is in the same state as a 4), and the air is further heated to state a5 of fig. 3.
The third step: the working medium flowing out of the second-stage condenser 9 flows through the second-stage throttle valve 10 to be throttled and depressurized, and becomes a gas-liquid two-phase state (as shown in a state 7 in a figure 3). The gas-liquid two-phase fluid at the working medium side outlet of the first-stage condenser 5 and the gas-liquid two-phase fluid at the outlet of the second-stage throttle valve 10 are mixed to a state 9 in a figure 3, then mixed with two streams of medium-pressure fluid (as a state 10 in a figure 3) flowing out from the working medium side outlet of the first-stage condenser 5 to a state 7 in a figure 3, further throttled to a state 11 in a figure 3 through the first-stage throttle valve 6, then enter the working medium side inlet of the evaporator 2, and the working medium absorbs heat to be in a saturated gas state (as a state 1 in a figure 3), and is absorbed by the first-stage compressor 3 to.
The fourth step: the wet air (as shown in state a3 of fig. 3) flowing out of the drying chamber 25 and performing heat and moisture exchange with the material flows into the air cooler 24 to release a part of sensible heat, so that the temperature of the wet air is initially reduced to state a2 of fig. 3, then flows into the evaporator 2, the temperature and the humidity are simultaneously reduced, at this time, the air is in a state with lower temperature and lower humidity (as shown in state a1 of fig. 3), then the air firstly flows into the first-stage condenser 5 to be heated to state a4(a6) of fig. 3, then the air enters the second-stage condenser 9 to be heated to state a5 of fig. 3, is continuously heated to a higher temperature, then enters the drying chamber, and after performing heat and moisture exchange with the material (as shown in state a3 of fig. 3), the air flows into the air cooler 24 to be cooled to state a2 of fig..
(3) If a non-azeotropic mixed working medium is adopted, the matching characteristic of the working medium of the double-stage compression heat pump double-condenser intermediate complete cooling heat pump drying system and the air heating process is more excellent, the system energy efficiency can be further improved, and the economic benefit is improved. The temperature-enthalpy diagram is shown in fig. 4.
The specific implementation mode is as follows:
the first step is as follows: the first stage compressor 3 sucks a low-temperature and low-pressure working medium (as shown in a state 1 in a figure 4) at an outlet at the working medium side of the evaporator 2, compresses the working medium into medium-temperature and medium-pressure superheated gas (as shown in a state 2 in a figure 4), the superheated gas flows into a working medium side inlet of the first stage gas cooler 4, and the gas is divided into two paths after the temperature is reduced (as shown in a state 3 in a figure 4) after the working medium in the first stage gas cooler 4 exchanges heat; one path of the refrigerant flows into a first-stage condenser 5 to be condensed into saturated liquid (as shown in a state 8 of a figure 4), then the refrigerant enters a first-stage throttle valve 6 to be throttled and decompressed into a two-phase fluid state (as shown in a state 10 of the figure 4), the gas-liquid two-phase fluid enters a refrigerant side inlet of the evaporator 2, the refrigerant is changed into a saturated gas state (as shown in a state 1 of the figure 4) after evaporating and absorbing the heat of humid air, and the saturated gas state is sucked by a first-.
The second step is that: the other path of superheated gas from the first stage gas cooler 4 flows into the second stage compressor 7, the working fluid is compressed into high temperature and high pressure fluid (as shown in state "4" in fig. 4), and then flows into the working fluid side inlet of the second stage condenser 9, the working fluid exchanges heat with the air flowing out of the first stage condenser 5 (as shown in states a5 and a6 in fig. 4, and states a5 and a6 are the same), and the heat exchange fluid is further heated to state a4 in fig. 4.
The third step: the working medium flowing out of the second-stage condenser 9 flows through the second-stage throttle valve 10 to be throttled and depressurized, and becomes a gas-liquid two-phase state (as shown in a state 8 in a figure 4). The gas-liquid two-phase fluid at the working medium side outlet of the first-stage condenser 5 and the gas-liquid two-phase fluid at the outlet of the second-stage throttle valve 10 are mixed to a state of 12 in a figure 4, then mixed with two streams of medium-pressure fluid (as the state of 12 in the figure 4) flowing out from the working medium side outlet of the first-stage condenser 5 to a state of 7 in the figure 3, further throttled to the state of 10 in the figure 4 through the first-stage throttle valve 6, then enter the working medium side inlet of the evaporator 2, and the working medium absorbs heat to be in a saturated gas state (as the state of 4 in the figure 4), and is absorbed by the first-.
The fourth step: the wet air (as shown in state a3 of fig. 4) flowing out of the drying chamber 25 and performing heat and moisture exchange with the material flows into the air cooler 24 to release a part of sensible heat, so that the temperature of the wet air is initially reduced to state a2 of fig. 4, then flows into the evaporator 2, the temperature and the humidity are simultaneously reduced, at this time, the air is in a state with lower temperature and lower humidity (as shown in state a1 of fig. 4), then the air firstly flows into the first-stage condenser 5 to be heated to state a6(a5) of fig. 4, then the air enters the second-stage condenser 9 to be heated to state a4 of fig. 4, is continuously heated to a higher temperature, then enters the drying chamber, and after performing heat and moisture exchange with the material (as shown in state a3 of fig. 4), the air flows into the air cooler 24 to be cooled to state a2 of fig..
Example two: the heat pump drying system is completely cooled in the middle of a plurality of condensers with three or more stages of compression.
The device can be designed into a complete heat pump drying system in the middle of a multi-stage compression multi-stage condenser according to specific implementation requirements, so that the air is dried for many times, and the requirements of drying processes of different materials are better met. An example of a specific multi-stage compression multi-stage condenser intermediate complete heat pump drying system is shown in fig. 5.
The specific implementation mode is as follows:
the first step is as follows: the first stage compressor 3 sucks the low-temperature and low-pressure working medium at the working medium side outlet of the evaporator 2, compresses the working medium into superheated gas with intermediate pressure, and then enters the first stage gas cooler 4 for heat exchange. Then divided into two paths. One path of hot gas flows into the working medium side of the first-stage condenser 5, the working medium in the condenser is condensed, and the wet air is heated to a certain temperature. Then the working medium enters a first-stage throttle valve 5 for throttling and pressure reduction, then enters the working medium side of the evaporator 2, and is sucked by a first-stage compressor 3 after the working medium absorbs heat and evaporates.
The second step is that: the other path of working medium flowing out of the first-stage gas cooler 4 firstly enters the second-stage compressor 7 and is compressed into superheated gas, the fluid flowing out of the second-stage compressor 7 flows into the working medium side of the second-stage condenser 8, then flows through the second-stage throttle valve 10, is throttled and depressurized, is changed into a gas-liquid two-phase state, exchanges heat with the air flowing out of the first-stage condenser 5, and the air is further heated. The heated air enters the third stage condenser. The fluid flowing out from the working medium side of the second-stage condenser 9 is mixed with the gas-liquid two-phase fluid from the third stage, and flows through the second-stage throttle valve 10 to be throttled and decompressed to become a gas-liquid two-phase state. The throttled and depressurized gas-liquid two-phase fluid is mixed with the fluid flowing out of the first-stage condenser 5 and then throttled by the first-stage throttle valve 6.
The third step: the structure form of the loop from the 3 rd stage to the n-1 th stage of the system is the same, and for simplifying the description, the 3 rd stage to the n-1 th stage are all represented by the ith stage. The working medium flowing out of the ith stage compressor firstly enters the ith stage gas cooler 11 for cooling, then enters the working medium side of the ith stage condenser 12 for heat exchange with the air flowing out of the (i-1) th stage gas cooler, the air is further heated, and the heated air enters the ith stage condenser. The fluid flowing out of the ith stage gas cooler 11 enters an i +1 th stage compressor, the working medium flowing out of the i +1 th stage compressor firstly enters an i +1 th stage gas cooler 15 for cooling and then enters the working medium side of an i +1 th stage condenser 16 for heat exchange with the fluid flowing out of the ith stage gas cooler, the air is further heated, and the heated air enters an i +2 th stage condenser. The working medium flowing out from the working medium side of the (i + 1) th-stage condenser 16 is throttled and depressurized by the (i + 1) th-stage throttle valve 17 to become a gas-liquid two-phase state. The fluid is mixed with the fluid flowing out from the working medium side of the i-th stage condenser 12, and then flows through the i-th stage throttle valve 13 for throttling.
The fourth step: the fluid flowing out of the nth-1 stage compressor enters the working medium side of the nth-1 stage gas cooler 18 for cooling, then enters the nth-stage compressor 21 for compressing into superheated gas, the superheated gas flowing out of the nth-stage compressor 21 flows into the working medium side of the nth-stage condenser 22 for exchanging heat with the air flowing out of the nth-1 stage condenser, and the air is heated for the last time.
The fifth step: the fluid flowing out of the working medium side of the n-1 stage gas cooler 18 is divided into two paths, and one path flows through the n-1 stage condenser 19. The working medium flowing out from the working medium side of the nth-stage condenser 22 flows through the nth-stage throttle valve 23 to be throttled and depressurized, and becomes a gas-liquid two-phase state. The two paths of fluid are mixed and then enter an n-1 level throttle valve for throttling.
And a sixth step: the hot air flowing out from the nth-stage condenser 22 enters the drying chamber 25 to perform heat and moisture exchange with the material, the air temperature is reduced, the moisture content is increased, the air is wet air at the moment, the wet air firstly flows into the air cooler 24 to release a part of sensible heat, so that the temperature of the wet air is preliminarily reduced, then the wet air flows into the evaporator 2, the temperature and the humidity are simultaneously reduced, the air is in a state that the temperature and the humidity are both lower at the moment, then the air sequentially flows into the condensers at all stages, and after the air is continuously heated to a higher temperature, the air enters the drying chamber 25 again, and the air side circulation is completed.
Although the preferred embodiments of the present invention have been described with reference to the accompanying drawings, the present invention is not limited to the above-mentioned embodiments, which are only illustrative and not restrictive, and those skilled in the art can make many forms without departing from the spirit and scope of the present invention, which is within the protection scope of the present invention.
Claims (2)
1. A multi-stage compression multi-condenser intermediate complete cooling heat pump drying system is characterized in that i is more than or equal to 3 and less than or equal to n-1, and n is more than or equal to 4 in the system;
the outlet of the first-stage compressor (3) is connected with the working medium side inlet of the first-stage gas cooler (4), the working medium side outlet of the first-stage gas cooler (4) is connected with the working medium side inlet of the first-stage condenser (5), the working medium side outlet of the first-stage condenser (5) is connected with the inlet of the first-stage throttle valve (6), the outlet of the first-stage throttle valve (6) is connected with the working medium side inlet of the evaporator (2), and the working medium side outlet of the evaporator (2) is connected with the inlet of the first-stage compressor (3); the working medium side outlet of the first-stage gas cooler (4) is connected with the inlet of a second-stage compressor (7), the outlet of the second-stage compressor (7) is connected with the working medium side inlet of a second-stage gas cooler (8), the working medium side outlet of the second-stage gas cooler (8) is connected with the inlet of a second-stage condenser (9), the outlet of the second-stage condenser (9) is connected with the inlet of a second-stage throttle valve (10), and the outlet of the second-stage throttle valve (10) is connected with the inlet of a first-stage throttle valve (6);
the working medium side outlet of the ith stage gas cooler (11) is connected with the inlet of an ith stage condenser (12), and the outlet of the ith stage condenser (12) is connected with the inlet of an ith stage compressor; the working medium side outlet of the ith stage gas cooler (11) is connected with the inlet of an i +1 th stage compressor (14), the outlet of the i +1 th stage compressor (14) is connected with the working medium side inlet of an i +1 th stage gas cooler (15), the working medium side outlet of the i +1 th stage gas cooler (15) is connected with the inlet of an i +1 th stage condenser (16), the outlet of the i +1 th stage condenser (16) is connected with the inlet of an i +1 th stage throttle valve (17), and the outlet of the i +1 th stage throttle valve (17) is connected with the inlet of an i +1 th stage throttle valve (13);
the outlet of the n-1 stage compressor is connected with the working medium side inlet of the n-1 stage gas cooler (18), the working medium side outlet of the n-1 stage gas cooler (18) is connected with the inlet of an n-1 stage condenser (19), the outlet of the n-1 stage condenser (19) is connected with the inlet of an n-1 stage throttle valve (20), and the working medium side outlet of the n-1 stage throttle valve (20) is connected with the inlet of an n-2 stage throttle valve; the working medium side outlet of the (n-1) th stage gas cooler (18) is connected with the inlet of the nth stage compressor (21), and the outlet of the nth stage compressor (21) is connected with the working medium side inlet of the nth stage condenser (22); an outlet of a working medium side of the nth-stage condenser (22) is connected with an inlet of an nth-stage throttle valve (23), and an outlet of the nth-stage throttle valve (23) is connected with an inlet of an n-1 st-stage throttle valve (20);
an outlet of the drying chamber (25) is connected with an air side inlet of an air cooler (24), an air side outlet of the air cooler (24) is connected with an air side inlet of an evaporator (2), an air side outlet of the evaporator (2) is connected with an air side inlet of a first-stage condenser (5), an air side outlet of the first-stage condenser (5) is connected with an air side inlet of a first-stage gas cooler (4), an air side outlet of the first-stage gas cooler (4) is connected with an air side inlet of a second-stage condenser (9), an air side outlet of the second-stage condenser (9) is connected with an air side inlet of a second-stage gas cooler (8), an air side outlet of the second-stage gas cooler (8) is connected with an air side inlet of a third-stage condenser, an air side outlet of the third-stage condenser is connected with an air side inlet of the third-stage gas cooler, an air side outlet of an n-1-stage gas cooler (18) is connected with an air side inlet of an nth-stage condenser, the air side outlet of the nth stage condenser (22) is connected with the inlet of the drying chamber (25).
2. The system of claim 1, wherein the working medium is pure refrigerant or CO2/R1234zeE、CO2/R1234zeZ、CO2Non-azeotropic mixtures of/R1234 yf, R41/R1234zeE, R41/R1234zeZ, R41/R1234yf, R32/R1234zeE, R32/R1234zeZ, R32/R1234 yf.
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110500876A (en) * | 2019-09-05 | 2019-11-26 | 天津商业大学 | A kind of more complete chiller-heat pump drying systems in condensers centre of multi-stage compression |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110500876A (en) * | 2019-09-05 | 2019-11-26 | 天津商业大学 | A kind of more complete chiller-heat pump drying systems in condensers centre of multi-stage compression |
| CN110500876B (en) * | 2019-09-05 | 2024-05-03 | 天津商业大学 | Multistage compression multi-condenser intermediate complete cooling heat pump drying system |
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