CN211119988U - Multistage compression multistage condensation intermediate flash incomplete cooling medium-high temperature heat pump system - Google Patents
Multistage compression multistage condensation intermediate flash incomplete cooling medium-high temperature heat pump system Download PDFInfo
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- CN211119988U CN211119988U CN201921465389.1U CN201921465389U CN211119988U CN 211119988 U CN211119988 U CN 211119988U CN 201921465389 U CN201921465389 U CN 201921465389U CN 211119988 U CN211119988 U CN 211119988U
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Abstract
The utility model provides a flash distillation under heat pump system in many temperature levels of incomplete cooling in middle of multistage compression multistage condensation. The utility model consists of an evaporator, compressors at all levels, condensers at all levels, throttle valves at all levels and gas-liquid separators at all levels, wherein the process comprises multistage continuous compression working medium heat pump circulation and normal temperature water continuous heating; the multistage compression multistage condensation intermediate flash incomplete cooling medium-high temperature heat pump system can be set into multiple stages (n stages for short) according to the process requirements, and the higher the temperature rise is, the more the number of stages is set. Through the multistage compression and the multistage condensation process of refrigerant, carry out a lot of continuous heating to normal atmospheric temperature water, can show the irreversible loss of heat transfer with the refrigerant in the normal atmospheric temperature water heating process that reduces, the compression of compressor at different levels is less. The heating hot water heating pipeline is connected in parallel between the condensers and can be used for heating rooms, so that the gradient utilization of heat is realized.
Description
Technical Field
The utility model relates to a heat pump technical field especially relates to a flash distillation under complete cooling medium-high temperature heat pump system in middle of multistage compression multistage condensation.
Background
The demands for medium-high temperature hot water and steam in life and industry are very wide, but the production of medium-high temperature hot water usually consumes a large amount of electric power and fuel resources. The heat pump product is widely used as a clean, efficient and stable heating device, and further the improvement of the energy efficiency of the heat pump device has important practical significance and social value in promoting energy conservation and emission reduction and improving economic benefits.
The condensing temperature of the conventional medium-high temperature heat pump system is constant, normal-temperature water is directly heated in the condenser, the temperature difference of an inlet and an outlet of the normal-temperature water is large and limited by the heat exchange temperature difference of a refrigerant of the condenser and the normal-temperature water, the heat exchange temperature difference distribution of fluids on two sides in the condenser is seriously uneven, the average heat exchange temperature difference in the condenser is large, large irreversible loss is generated in the heat exchange process, and the energy efficiency of the system is low. The conventional single-stage compression heat pump system using the non-azeotropic working medium has equivalent temperature slippage in the evaporation and condensation processes, 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, but for a medium-high temperature heat pump system, the temperature change at the heat source side is generally small, the temperature rise of water or steam at the heat sink side is large or large, and the temperature drop of the fluid at the heat source side is far larger than that of the fluid at the heat source side. 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 a flash distillation under heat pump system in multi-stage compression multi-stage condensation middle-temperature level to solve the problem that heat transfer process irreversible loss is big, compression ratio is big and the system efficiency is low.
The utility model adopts the technical proposal that:
the method comprises the following steps that a multistage compression multistage condensation intermediate flash incomplete cooling multi-temperature stage medium-high temperature heat pump system comprises a multistage continuous compression working medium heat pump cycle and a normal temperature water continuous heating process; the multistage compression multistage condensation intermediate flash incomplete cooling medium-high temperature heat pump system can be set into multiple stages (n stages for short) according to the process requirements, and the higher the temperature rise is, the more the number of stages is set.
A multi-stage compression multi-stage condensation intermediate flash incomplete cooling medium-high temperature heat pump system, wherein 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 condenser 4, the working medium side outlet of the first-stage compressor 3 is connected with the inlet of the second-stage compressor 6, the working medium side outlet of the first-stage condenser 4 is connected with the inlet of the first-stage throttle valve 5, the outlet of the second-stage gas-liquid separator 9 is connected with the inlet of the first-stage throttle valve 5, the outlet of the first-stage throttle valve 5 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; the normal temperature water outlet is connected with the heat exchange fluid side inlet of the second-stage condenser 7, the heat exchange fluid side outlet of the second-stage condenser 7 is connected with the heat exchange fluid (hot water or steam) side inlet of the third-stage condenser, the heat exchange fluid side outlet of the i-th-stage condenser 11 is connected with the heat exchange fluid side inlet of the n-th-stage condenser 15, and the heat exchange fluid side outlet of the n-th-stage condenser 15 is connected with the medium-high temperature hot water or high-temperature steam inlet;
the outlet of the i-1 stage compressor is connected with the inlet of the i-stage compressor, the i-stage gas-liquid separator is connected with the inlet of the i-stage compressor, the outlet of the i-stage compressor is connected with the inlet of the i +1 stage compressor, the outlet of the i-stage compressor is connected with the working medium side inlet of the i-stage condenser, the working medium side outlet of the i-stage condenser is connected with the inlet of the i-stage throttle valve, the outlet of the i +1 stage gas-liquid separator is connected with the inlet of the i-stage throttle valve, the outlet of the i-stage throttle valve is connected with the inlet of the i-stage gas-liquid separator, and the outlet of the i-stage gas-liquid separator is connected with;
the outlet of the n-1 stage compressor is connected with the inlet of the n-1 stage compressor 14, the outlet of the side of the n-stage gas-liquid separator 17 is connected with the inlet of the n-stage compressor 14, the outlet of the n-stage compressor 14 is connected with the inlet of the working medium side of the n-stage condenser 15, the outlet of the working medium side of the n-stage condenser 15 is connected with the inlet of the n-stage throttle valve 16, the outlet of the n-stage throttle valve 16 is connected with the inlet of the n-stage gas-liquid separator 17, and the outlet of the n-stage gas-liquid separator 17 is connected with the inlet of the n.
And (3) allowing the normal-temperature water to sequentially flow into each temperature-level condenser for heating, and continuously heating to the process design temperature to obtain medium-high-temperature hot water or high-temperature steam required by the process, thereby completing the continuous heating process of the normal-temperature water.
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 system can also connect each temperature-stage condenser in parallel with a heating hot water heating pipeline, and is applied to a multi-stage compression multi-stage condensation intermediate flash incomplete cooling heat pump two-combined supply system. The heat supply end can be provided with a fan coil, a ground coil, a radiator and other devices, and each stage of condenser directly provides heat for the condenser, so that the condenser is used for heating rooms, and the gradient utilization of heat is realized.
Compared with the prior art, the utility model has the advantages and positive effect be:
(1) compare with conventional pure quality single-stage compression heat pump system, the utility model discloses well normal atmospheric temperature water heats in succession in multistage condenser, and water is at condensation at different levelsThe temperature rise in the device is low, the condensing process of each temperature position of the refrigerant and the heating process of normal temperature water form good temperature matching, the heat exchange temperature difference between the heat exchange fluid and the working medium can be obviously reduced, the irreversible loss of heat exchange between the heat exchange fluid and the refrigerant is reduced,
the efficiency is improved, and the energy efficiency of the system 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 temperature of a heat exchange fluid. Compare with conventional non-azeotropic medium single-stage compression heat pump system, the utility model discloses the heating process of normal atmospheric temperature water 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 less the gas absorption amount of the compressor is, and compared with a single-stage heat pump system under the condition of the same normal temperature water temperature rise, the power consumption of the compressor is obviously reduced, and the manufacturing cost of the compressor is reduced;
(4) compared with the traditional single-stage compression, the pressure ratio in the multi-stage compression process is reduced, and the isentropic efficiency of the compressor is improved. In addition, the device of the utility model is provided with an intermediate flash process to cool the superheated gas at the outlet of the compressor, the exhaust temperature is reduced, and the service life of the compressor is prolonged;
(5) the device can be used for heating, producing domestic hot water, industrial medium-high temperature hot water, high pressure steam and the like. Has wide application and good development prospect.
Drawings
FIG. 1 is a diagram of a two-stage compression double-condenser intermediate flash incomplete cooling medium-high temperature heat pump system;
FIG. 2 is a temperature-enthalpy diagram of a high-temperature heat pump system in a double-stage pure compression double-condenser intermediate flash incomplete cooling mode;
FIG. 3 is a temperature-enthalpy diagram of a high-temperature heat pump system in the intermediate flash incomplete cooling of a double-stage non-azeotropic working medium compression double condenser;
FIG. 4 is a diagram of a two-stage compression double-condenser intermediate flash incomplete cooling heat pump two-combined supply system;
FIG. 5 is a diagram of a multi-stage compression multi-stage condenser intermediate flash incomplete cooling medium-high temperature heat pump system.
Detailed Description
The first embodiment is as follows: intermediate flash incomplete cooling medium-high temperature heat pump system with double-stage compression double condensers
The system consists of a first-stage heat pump cycle, a second-stage heat pump cycle and a normal-temperature water continuous heating process, and is shown in figure 1.
(1) If the system adopts pure working media, the temperature-enthalpy diagram of the middle-high temperature heat pump system in the middle flash incomplete cooling of the double-stage pure compression double-condenser 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 a state 1 of a figure 2) at the working medium side outlet of the evaporator 2, compresses the working medium into medium-temperature and medium-pressure superheated gas (as shown in a state 2 of the figure 2), and then divides the superheated gas into two paths. One path of gas flows into a working medium side inlet of the first-stage condenser 4, the working medium in the condenser is condensed to saturated liquid (as shown in a state 10 in a figure 2), and normal-temperature water (as shown in a state w1 in the figure 2) is heated to a certain temperature (as shown in a state w2 in the figure 2). Then the working medium enters the first-stage throttle valve 5 to be throttled and depressurized to a two-phase fluid state (as shown in a state 11 of figure 2), the gas-liquid two-phase fluid enters the working medium side inlet of the 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 normal-temperature water, and the saturated gas state is sucked by the first-stage compressor 3.
The second step is that: the other path of superheated gas flowing out of the first-stage compressor 3 flows into the second-stage compressor 6, the working medium is compressed into high-temperature and high-pressure fluid (as shown in the state 4 of fig. 2), and then flows into the working medium side inlet of the second-stage condenser 7, the working medium exchanges heat with the heat exchange fluid (hot water or steam) flowing out of the heat exchange fluid side of the first-stage condenser (as shown in the states w2 and w3 of fig. 2, and w2 and w3 are in the same state), and the heat exchange fluid is further heated to the state w4 of fig. 2.
The third step: the working medium (as shown in the state 6 of the figure 2) flowing out of the second-stage condenser 7 flows through the second-stage throttle valve 8 to be throttled and decompressed to be in a gas-liquid two-phase state (as shown in the state 7 of the figure 2), and then flows into the gas-liquid separator 9 to separate gas from liquid. Working medium at the outlet of the gas-liquid separator 9 is divided into two paths (saturated gas and saturated liquid), one path of saturated gas (as shown in a state 8 in a figure 2) is mixed with medium-pressure superheated gas at the outlet of the first-stage compressor 3, enters the second-stage compressor 6 to be compressed into high-temperature high-pressure gas (as shown in a state 4 in a figure 2), the other path of saturated liquid (as shown in a state 10 in a figure 2) is converged with saturated liquid at the working medium side outlet of the first-stage condenser 4, enters the first-stage throttle valve 5 to be throttled to a state 11 in a figure 2 and then enters the working medium side inlet of the evaporator 2, and the working medium absorbs heat to become saturated gaseous state (.
The fourth step: the normal temperature water (as shown in the state w1 in fig. 2) firstly flows into the heat exchange fluid side of the first-stage condenser 4 to be heated to the state w2(w3) in fig. 2, and then flows into the heat exchange fluid side inlet of the second-stage condenser 7 (as shown in the state w3 in fig. 2) to be heated to the temperature required by the process (as shown in the state w4 in fig. 2), so that the required medium-high temperature hot water or high temperature steam is obtained, and the continuous heating process of the normal temperature water is completed.
(2) If a non-azeotropic mixed working medium is adopted, the matching characteristic of the refrigerant of the high-temperature heat pump system in the incomplete intermediate flash evaporation cooling of the double-stage compression double-condenser and the normal-temperature water heating process is more excellent, the system energy efficiency can be further improved, and the economic benefit can be improved. The temperature-enthalpy diagram of the high-temperature heat pump system in the intermediate flash incomplete cooling of the double-stage non-azeotropic working medium compression double-condenser is shown in figure 3.
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 a state 1 of a figure 3) at the working medium side outlet of the evaporator 2, compresses the working medium into medium-pressure superheated gas (as shown in a state 2 of a figure 3), and then divides the gas into two paths. One path flows into a working medium side inlet of the first-stage condenser 4, the working medium in the condenser is condensed to saturated liquid (as shown in a state 8 in figure 3), and normal-temperature water (as shown in a state w1 in figure 3) on the heat exchange fluid side is heated to a certain temperature (as shown in a state w2 in figure 3). Then the working medium enters the first-stage throttle valve 5 to be throttled and depressurized to a two-phase fluid state (as shown in a state 11 of figure 3), the gas-liquid two-phase fluid enters the working medium side inlet of the evaporator 2, and the working medium is changed into a saturated gas state (as shown in a state 1 of figure 3) after absorbing the heat of the normal-temperature water and is sucked by the first-stage compressor 3.
The second step is that: and the other gas flowing out of the first-stage compressor 3 flows into the second-stage compressor 6, the working fluid is compressed into high-temperature and high-pressure fluid (as shown in the state 4 in the figure 3), flows into the working fluid side inlet of the second-stage condenser 7, exchanges heat with the heat exchange fluid flowing out of the heat exchange fluid side of the first-stage condenser 4 (as shown in the states w2 and w3 in the figure 3, and the states w2 and w3 are the same), and is further heated to the state w4 in the figure 3.
The third step: working medium (as shown in the state 6 of the figure 3) flowing out of the second-stage condenser 7 flows through the second-stage throttle valve 8 to be throttled and decompressed, and becomes a gas-liquid two-phase state (as shown in the state 7 of the figure 3). The working medium flows into the gas-liquid separator 9 again for gas-liquid separation. Working medium at the outlet of the gas-liquid separator 9 is divided into two paths (saturated gas and saturated liquid), one path of saturated gas (as shown in a state 10 in figure 3) is mixed with medium-pressure superheated gas at the outlet of the first-stage compressor 3, enters the second-stage compressor 6 to be compressed into high-temperature high-pressure gas (as shown in a state 4 in figure 3), the other path of saturated liquid (as shown in a state 8 in figure 3) is converged with saturated liquid at the working medium side outlet of the first-stage condenser 4, enters the first-stage throttle valve 5 to be throttled to a state 11 in figure 3, enters the working medium side inlet of the evaporator 2, and is sucked by the first-stage compressor 3 after heat absorption and evaporation.
The fourth step: the normal temperature water (as shown in state w1 in fig. 3) firstly flows into the heat exchange fluid side of the first-stage condenser 4 to be heated to state w2(w3) in fig. 3, then flows into the heat exchange fluid side of the second-stage condenser 7 to be continuously heated (as shown in state w4 in fig. 3), and is continuously heated to the medium-high temperature to obtain medium-high temperature hot water or high-temperature steam required by the process, so that the continuous heating process of the normal temperature water is completed.
Example two: two ends of the first-stage condenser are connected with a heating hot water heating pipeline in parallel to form a two-stage compression double-condenser intermediate flash incomplete cooling heat pump two-combined-supply system, and the system is shown in fig. 4.
The heat supply end 10 can be provided with a fan coil, a ground coil, a radiator and other heat supply ends, normal-temperature heat exchange fluid at an outlet of the heat supply end 10 enters the heat exchange fluid side of the first-stage condenser 4 and is heated to a certain temperature for the first time, return water at the heat supply end exchanges heat with high-temperature working media flowing out of the first-stage compressor 3, the exhaust temperature of the first-stage compressor 3 is reduced, the return water at the heat supply end is further heated and used for heating rooms, the heat gradient utilization is realized, and the heat loss is reduced.
Example three: the intermediate flash evaporation of three-stage and above compressed multiple condensers incompletely cools the medium-high temperature heat pump system.
The device can be designed into a multi-stage compression multi-stage condenser intermediate flash incomplete cooling medium-high temperature heat pump system according to specific implementation requirements, and normal temperature water is heated for many times to prepare hot water or steam with higher temperature so as to better meet the requirements of different processes. The intermediate flash evaporation incomplete cooling medium-high temperature heat pump system of the multistage compression multistage condenser is shown in a figure 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 1, compresses the working medium into superheated gas with intermediate pressure, and then divides the working medium into two paths. One path of hot gas flows into the working medium side of the first-stage condenser 4, the working medium in the condenser is condensed, and the normal-temperature water 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 1, and is sucked by a first-stage compressor 3 after the working medium absorbs heat and evaporates.
The second step is that: the other way of working medium flowing out of the first-stage compressor 3 is mixed with saturated gas in the second-stage gas-liquid separator and then enters the second-stage compressor 6 to be compressed into superheated gas, fluid flowing out of the second-stage compressor 6 is divided into two ways, one way of fluid flows into the working medium side of the second-stage condenser 7 to exchange heat with normal-temperature water flowing out of the heat exchange fluid side of the first-stage condenser 4, and the normal-temperature water is further heated. The heated normal temperature water enters the heat exchange fluid side of the third-stage condenser. The fluid flowing out from the working medium side of the second-stage condenser 7 is mixed with the gas-liquid two-phase fluid from the third stage, flows through the second-stage throttle valve 8, is throttled and depressurized, is changed into a gas-liquid two-phase state, and enters the second-stage gas-liquid separator 9 to separate gas from liquid. The working medium at the outlet of the second-stage gas-liquid separator 9 is divided into two paths (saturated gas and saturated liquid), one path of saturated gas is mixed with the medium-pressure superheated gas at the outlet of the first-stage compressor 3 and enters the second-stage compressor 6, and the other path of saturated liquid is converged with the saturated liquid at the working medium side outlet of the first-stage condenser 4 and enters the first-stage throttle valve 5 for throttling. The other flow from the second stage compressor 6 enters the third stage compressor.
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. And the other path of working medium flowing out of the i-1 stage compressor enters the i-1 stage compressor 10 to be compressed into superheated gas, the superheated gas flowing out of the i-1 stage compressor 10 is divided into two paths, one path of the superheated gas flows into the working medium side of the i-1 stage condenser and exchanges heat with the heat exchange fluid flowing out of the heat exchange fluid side of the i-1 stage condenser, the heat exchange fluid is further heated, and the heated normal-temperature water enters the heat exchange fluid side of the i +1 stage condenser. The mixed fluid flowing out from the working medium side of the i-th stage condenser 11 and the saturated liquid from the i +1 th stage are throttled and depressurized by the i-th stage throttle valve 12 to be in a gas-liquid two-phase state, and then enter the i-th stage gas-liquid separator 13 to separate gas from liquid, the working medium at the outlet of the i-th stage gas-liquid separator 13 is divided into two paths (saturated gas and saturated liquid), one path of saturated gas is mixed with the medium-pressure superheated gas at the outlet of the i-1-th stage first stage compressor and enters the i-th stage second stage compressor 10, and the other path of saturated liquid is converged with the saturated liquid at the outlet of the working medium side of the i-1-th stage first stage condenser and. The other flow from the i-th stage compressor 10 enters the i + 1-th stage compressor to be compressed.
The fourth step: and the other path of fluid flowing out of the n-1 stage compressor enters the n-stage compressor 14 to be compressed into superheated gas, the superheated gas flowing out of the n-stage compressor 14 flows into the working medium side of the n-stage condenser 15 to exchange heat with the heat exchange fluid flowing out of the heat exchange fluid side of the n-1 stage condenser, and the heat exchange fluid is heated for the last time.
The fifth step: the fluid flowing out of the working medium side of the nth-stage condenser 15 flows through the nth-stage throttle valve 16, is throttled and depressurized to become a gas-liquid two-phase state, and then enters the nth-stage gas-liquid separator 17 to separate gas from liquid. Working medium at the outlet of the nth stage gas-liquid separator 17 is divided into two paths (saturated gas and saturated liquid), one path of saturated gas is mixed with medium-pressure superheated gas at the outlet of the nth-1 stage first stage compressor and enters the nth stage second stage compressor 14, and the other path of saturated liquid is converged with saturated liquid at the outlet of the working medium side of the nth-1 stage first stage condenser and enters the nth-1 stage first stage throttle valve for throttling.
And a sixth step: the normal temperature water flows into each stage of condenser in sequence, and flows out from the heat exchange fluid side of the nth stage of condenser 17 after being continuously heated to the medium-high temperature, so as to obtain medium-high temperature hot water or high temperature steam required by the process, and complete the continuous heating process of the normal temperature water.
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-stage condensation intermediate flash incomplete cooling medium-high temperature heat pump 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 condenser (4), the working medium side outlet of the first-stage compressor (3) is connected with the inlet of the second-stage compressor (6), the working medium side outlet of the first-stage condenser (4) is connected with the inlet of the first-stage throttle valve (5), the outlet of the second-stage gas-liquid separator (9) is connected with the inlet of the first-stage throttle valve (5), the outlet of the first-stage throttle valve (5) 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; the normal-temperature water outlet is connected with a heat exchange fluid side inlet of a second-stage condenser (7), a heat exchange fluid side outlet of the second-stage condenser (7) is connected with a heat exchange fluid side inlet of a third-stage condenser, heat exchange fluid is hot water or steam, a heat exchange fluid side outlet of an i-th-stage condenser (11) is connected with a heat exchange fluid side inlet of an n-th-stage condenser (15), and a heat exchange fluid side outlet of the n-th-stage condenser (15) is connected with a middle-high temperature hot water or high-temperature steam inlet;
an outlet of the i-1 stage compressor is connected with an inlet of the i-1 stage compressor (10), an i-th stage gas-liquid separator (13) is connected with an inlet of the i-th stage compressor (10), an outlet of the i-th stage compressor (10) is connected with an inlet of the i +1 stage compressor, an outlet of the i-th stage compressor (10) is connected with a working medium side inlet of an i-th stage condenser (11), a working medium side outlet of the i-th stage condenser (11) is connected with an inlet of an i-th stage throttling valve (12), an outlet of the i +1 stage gas-liquid separator is connected with an inlet of the i-th stage throttling valve (12), an outlet of the i-th stage throttling valve (12) is connected with an inlet of the i-th stage gas-liquid separator (13), and an outlet of the i-th stage gas-liquid separator;
the outlet of the n-1 stage compressor is connected with the inlet of the n-1 stage compressor (14), the outlet of the side of the n-stage gas-liquid separator (17) is connected with the inlet of the n-stage compressor (14), the outlet of the n-stage compressor (14) is connected with the working medium side inlet of the n-stage condenser (15), the working medium side outlet of the n-stage condenser (15) is connected with the inlet of the n-stage throttle valve (16), the outlet of the n-stage throttle valve (16) is connected with the inlet of the n-stage gas-liquid separator (17), and the outlet of the n-stage gas-liquid separator (17) is connected with the inlet of the n-1 stage throttle valve.
2. The system as claimed in 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 |
|---|---|---|---|---|
| CN110486942A (en) * | 2019-09-05 | 2019-11-22 | 天津商业大学 | The not exclusively cooling moderate and high temperature heat system of multi-stage compression multi-stage condensing intermediate flash |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110486942A (en) * | 2019-09-05 | 2019-11-22 | 天津商业大学 | The not exclusively cooling moderate and high temperature heat system of multi-stage compression multi-stage condensing intermediate flash |
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