CN211119989U - Multi-stage compression multi-condenser intermediate throttling incomplete cooling medium-high temperature heat pump system - Google Patents
Multi-stage compression multi-condenser intermediate throttling incomplete cooling medium-high temperature heat pump system Download PDFInfo
- Publication number
- CN211119989U CN211119989U CN201921465734.1U CN201921465734U CN211119989U CN 211119989 U CN211119989 U CN 211119989U CN 201921465734 U CN201921465734 U CN 201921465734U CN 211119989 U CN211119989 U CN 211119989U
- Authority
- CN
- China
- Prior art keywords
- stage
- outlet
- condenser
- inlet
- throttle valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Images
Landscapes
- Heat-Pump Type And Storage Water Heaters (AREA)
Abstract
The utility model discloses a throttle incomplete cooling medium and high temperature heat pump system in middle of multi-stage compression multi-condenser. The utility model discloses by the evaporimeter, the compressor at all levels, condenser at all levels, choke valve at all levels, bypass choke valve and regenerator at all levels are constituteed, the i-1 st grade compressor links to each other with the ith grade regenerator, the ith grade regenerator links to each other with the ith grade compressor, the ith grade compressor links to each other with the (i + 1) th grade regenerator, the ith grade compressor links to each other with the ith grade condenser, the ith grade condenser is connected with the ith grade choke valve, the (i + 1) th grade choke valve links to each other with the ith grade choke valve, the (i + 1) th grade regenerator links to each other with the ith grade choke valve, the ith grade choke valve links to each other with the (i-1) th grade choke valve; the ith stage condenser is connected with an ith stage bypass throttle valve, the ith stage bypass throttle valve is connected with an ith stage heat regenerator, and the ith stage heat regenerator is connected with an (i-1) th stage throttle valve. The normal temperature water is heated according to the process requirements by setting different stages.
Description
Technical Field
The utility model relates to a heat pump technology field especially relates to a throttle incomplete cooling medium-high temperature heat pump system in middle of multistage compression multi-condenser.
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 an adopt multistage compression multistage condensation medium-high temperature heat pump system 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 relates to a technical scheme that throttle under-cooling medium-high temperature heat pump system took in middle of the many condensers of multistage compression is: i is more than or equal to 3 and less than or equal to n-1 in the system, and 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 condenser 4, the working medium side outlet of the first-stage compressor 3 is connected with the superheated gas side inlet of the second-stage heat regenerator 6, the superheated gas side outlet of the second-stage heat regenerator 6 is connected with the second-stage compressor 8, 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 throttle valve 11 is connected with the inlet of the first-stage throttle valve 5, the two-phase fluid side outlet of the second-stage heat regenerator 6 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; the working medium side outlet of the second-stage condenser 9 is connected with a second-stage heat regenerator 6 through a pipeline provided with a second-stage bypass throttle valve 7;
the outlet of the i-1 stage compressor is connected with the superheated gas side inlet of an i-stage heat regenerator 12, the superheated gas side outlet of the i-stage heat regenerator 12 is connected with the inlet of an i-stage compressor 13, the outlet of the i-stage compressor 13 is connected with the superheated gas side inlet of an i +1 stage heat regenerator, the outlet of the i-stage compressor 13 is connected with the working medium side inlet of an i-stage condenser 15, the working medium side outlet of the i-stage condenser 15 is connected with the inlet of an i-stage throttle valve 16, the outlet of the i +1 stage throttle valve is connected with the inlet of an i-stage throttle valve 16, the two-phase fluid side outlet of the i +1 stage heat regenerator is connected with the inlet of the i-stage throttle valve 16, and the outlet of the i-stage throttle valve 16 is connected with the; an outlet of a working medium side of an ith-stage condenser 15 is connected with an inlet of an ith-stage bypass throttle valve 14, an outlet of the ith-stage bypass throttle valve 14 is connected with a two-phase fluid side inlet of an ith-stage heat regenerator 12, and a two-phase fluid side outlet of the ith-stage heat regenerator 12 is connected with an inlet of an (i-1) th-stage throttle valve;
the outlet of the (n-1) th-stage compressor is connected with the inlet of the superheated gas side of the nth-stage heat regenerator 18, the outlet of the superheated gas side of the nth-stage heat regenerator 18 is connected with the inlet of the nth-stage compressor 19, the outlet of the nth-stage compressor 19 is connected with the inlet of the working medium side of the nth-stage condenser 17, the outlet of the working medium side of the nth-stage condenser 17 is connected with the inlet of the nth-stage throttle valve 10, and the outlet of the nth-stage throttle valve 10 is connected with the inlet of the nth-1 st-stage throttle valve; the working medium side outlet of the nth-stage condenser 17 is connected with the inlet of an nth-stage bypass throttle valve 20, the outlet of the nth-stage bypass throttle valve 20 is connected with the two-phase fluid side inlet of an nth-stage heat regenerator 18, and the two-phase fluid side outlet of the nth-stage heat regenerator 18 is connected with the inlet of an n-1 st-stage throttle valve;
the normal temperature water outlet is connected with the heat exchange fluid side inlet of the first-stage condenser 4, the heat exchange fluid side outlet of the first-stage condenser 4 is connected with the heat exchange fluid side inlet of the second-stage condenser 9, the heat exchange fluid side outlet of the second-stage condenser 9 is connected with the heat exchange fluid side inlet of the third-stage condenser, the heat exchange fluid side outlet of the ith-stage condenser 15 is connected with the heat exchange fluid side inlet of the (i + 1) th-stage condenser, the heat exchange fluid side inlet of the (n-1) th-stage condenser is connected with the heat exchange fluid side inlet of the nth-stage condenser 17, and the heat exchange fluid side outlet of the nth-stage condenser 17 is connected with.
The working medium is pure refrigerant or 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 multistage compression multi-condenser intermediate throttling 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.
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 regenerator, and the application is throttle incomplete 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 provided with a fan coil, a ground coil, a radiator and other devices, and each level of condenser and each level of heat regenerator directly provide heat for the condenser and the heat regenerator, so that the heat can be supplied to a room, and the gradient utilization of the heat can be realized.
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 normal-temperature water in the heat pump system is continuously heated in the multistage condenser, the temperature rise of the water in each stage of condenser is lower, the condensing process of each temperature position of the refrigerant and the heating process of the 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 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 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;
(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 throttling process to cool the hot 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 throttling incomplete cooling medium and high temperature heat pump system;
FIG. 2 is a temperature-enthalpy diagram of a high-temperature heat pump system in a two-stage pure compression double-condenser intermediate throttling incomplete cooling mode;
FIG. 3 is a temperature-enthalpy diagram of a two-stage non-azeotropic working medium compression double-condenser intermediate throttling incomplete cooling medium-high temperature heat pump system;
FIG. 4 is a diagram of a two-stage compression double condenser intermediate throttling under-cooled heat pump two-combined-supply system;
FIG. 5 is a diagram of a multi-stage compression multi-stage condenser intermediate throttle under-cooling medium-high temperature heat pump 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 throttling incomplete cooling medium-high temperature heat pump system
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 high-temperature heat pump system in the middle throttling 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 12 in a 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 in a 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 heat regenerator 6 to be cooled to the state 3 in fig. 2, then enters the second-stage compressor 8, the working medium is compressed into high-temperature and high-pressure fluid (as shown in the state 4 in fig. 2), and then flows into the working medium side inlet of the second-stage condenser 9, 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 in fig. 2, and w2 and w3 are in the same state), the temperature is reduced to the state 6 in fig. 2, and the heat exchange fluid is further heated to the state w 539.
The third step: the working medium flowing out of the second-stage condenser 9 is also divided into two paths, and one path of working medium flows through the second-stage bypass throttle valve 7 to be throttled and decompressed and becomes a gas-liquid two-phase fluid state (as shown in a state 7 in figure 2). The gas-liquid two-phase fluid after throttling and pressure reduction and high-temperature gas flowing out of the first-stage compressor 3 exchange heat in the heat regenerator 6, the exhaust temperature of the first-stage compressor is reduced to be in a state 3 in a figure 2, and the gas-liquid two-phase fluid absorbs heat and evaporates to be in a saturated gas state as in a state 8 in the figure 2. The other path of working medium flowing out of the second-stage condenser 9 flows through a 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 2). Saturated gas at the outlet of the working medium side of the heat regenerator 6 and gas-liquid two-phase fluid at the outlet of the throttle valve 10 are mixed to a state 9 in the figure 2, then mixed with three streams of medium-pressure fluid (as shown in a state 10 in the figure 2) flowing out from the outlet of the working medium side of the first-stage condenser 4 to a state 11 in the figure 2, further throttled to a state 12 in the figure 2 by flowing through the first-stage throttle valve 5, then enter the inlet of the working medium side of the evaporator 2, and the working medium absorbs heat to be in a saturated gas state (as shown in a state 1 in the figure 2), and is absorbed.
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 9 (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 double-stage compression double-condenser intermediate throttling incomplete cooling medium-high temperature heat pump system and the normal temperature water in the heating process is more excellent, the system energy efficiency can be further improved, and the economic benefit is improved. The temperature-enthalpy diagram of the high-temperature heat pump system in the two-stage non-azeotropic working medium compression double-condenser intermediate throttling incomplete 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 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 11 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 12 in 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 in 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: the other gas from the first stage compressor 3 flows into the regenerator 6 to be cooled to the state 3 in fig. 3 from the superheated gas side, and then enters the second stage compressor 8, the working fluid is compressed into high-temperature and high-pressure fluid (as shown in the state 4 in fig. 3), flows into the working fluid side inlet of the second stage condenser 9, exchanges heat with the heat exchange fluid flowing out from the heat exchange fluid side of the first stage condenser 4 (as shown in the states w2 and w3 in fig. 3, and the states w2 and w3 are the same), the temperature is reduced to the state 6 in fig. 3, and the heat exchange fluid is further heated to the state w4 in fig. 3.
The third step: the working medium flowing out of the second-stage condenser 9 is also divided into two paths, and one path of working medium flows through the second-stage bypass throttle valve 7 to be throttled and decompressed and becomes a gas-liquid two-phase fluid state (as shown in a state 7 in a figure 3). The gas-liquid two-phase fluid after throttling and pressure reduction and the high-temperature working medium flowing out of the first-stage compressor 1 exchange heat in the heat regenerator 6, the exhaust temperature of the first-stage compressor is reduced to a state 3 in a figure 3, and the gas-liquid two-phase fluid absorbs heat and evaporates to be in a saturated gas state (as a state 10 in the figure 3). The other path of working medium flowing out of the second-stage condenser 9 flows through a second-stage throttle valve 10 to be throttled and decompressed, and becomes a gas-liquid two-phase state (as shown in a state 7 in a figure 3). Saturated gas 7 at the outlet of the working medium side of the heat regenerator 6 and gas-liquid two-phase fluid 10 at the outlet of the throttle valve 10 are mixed to a state 9 in the figure 3, then mixed with three streams of medium-pressure working medium (as a state 11 in the figure 3) flowing out from the first-stage condenser 4 to a state 8 in the figure 3, further throttled to a state 12 in the figure 3 by flowing through the first-stage throttle valve 5, enter the evaporator 2, and are sucked by the first-stage compressor 3 after heat absorption and evaporation (as a state 1 in the figure 3) to finish heat pump circulation.
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 9 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: a heating hot water heating pipeline is connected in parallel between the condenser and the heat regenerator to form a double-stage compression double-condenser middle throttling incomplete cooling heat pump double-combined supply system, and the system is shown in figure 4.
The heat supply end 11 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 11 enters the heat exchange fluid side of the first-stage condenser 4 and is heated to a certain temperature for the first time and then flows into the heat exchange fluid side of the heat regenerator 6, 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, heat gradient utilization is achieved, and heat loss is reduced.
Example three: the intermediate throttling incomplete cooling medium-high temperature heat pump system of the multi-condenser with three-stage and above compression.
The device can also be designed into a multi-stage compression multi-stage condenser intermediate throttling incomplete cooling medium-high temperature heat pump system according to specific implementation requirements, so that normal temperature water is heated for many times to prepare hot water or steam with higher temperature, and requirements of different processes are better met. The intermediate throttling incomplete cooling medium-high temperature heat pump system of the multi-stage compression multi-stage condenser is shown in 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 2, 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 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 compressor 3 firstly enters the working medium side of the second-stage heat regenerator 6 for cooling and then enters the second-stage compressor 8 for compressing into superheated gas, the fluid flowing out of the second-stage compressor 8 is divided into two paths, one path of fluid flows into the working medium side of the second-stage condenser 9 and exchanges heat with the 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 9 is mixed with the gas-liquid two-phase fluid from the third stage, and then is divided into two paths. One path of the gas flows through a second-stage bypass throttle valve 7 for throttling and pressure reduction, and the gas phase and the liquid phase are changed into a gas-liquid two-phase state. The gas-liquid two-phase fluid after throttling and pressure reduction and the overfire gas flowing out of the first-stage compressor 3 exchange heat in the second-stage heat regenerator 6, the exhaust temperature of the first-stage compressor is reduced, and the gas-liquid two-phase fluid absorbs heat and evaporates into a saturated gas state. The other path of working medium flowing out of the second-stage condenser 9 flows through a second-stage throttle valve 11 for throttling and pressure reduction, and becomes a gas-liquid two-phase state. The two paths of fluid are mixed with the fluid flowing out from the working medium side of the first-stage condenser 4 and then flow through the first-stage throttle valve 5 for throttling. The other flow from the second stage compressor 8 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. The other path of working medium flowing out of the i-1 stage compressor firstly enters the heat exchange fluid side of the i-stage heat regenerator 12 for cooling, then enters the i-stage compressor 13 for compressing into superheated gas, the superheated gas flowing out of the i-stage compressor 13 is divided into two paths, one path of working medium flows into the working medium side of the i-stage condenser 15 to exchange 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 fluid flowing out of the working medium side of the i-th stage condenser 15 is mixed with the gas-liquid two-phase fluid from the (i + 1) th stage, and then is divided into two paths. One path of the gas flows through the i-th stage bypass throttle valve 14 for throttling and pressure reduction, and the gas phase and the liquid phase are changed into a gas-liquid two-phase state. The throttled and depressurized gas-liquid two-phase fluid and the superheated gas flowing out of the i-1 stage compressor exchange heat in the i-stage heat regenerator 12, the exhaust temperature of the i-1 stage compressor is reduced, and the gas-liquid two-phase fluid absorbs heat and evaporates into a saturated gas state. The other path of working medium flowing out from the working medium side of the i-th stage condenser 15 flows through the i-th stage throttle valve 16 for throttling and pressure reduction, and becomes a gas-liquid two-phase state. The two paths of fluid are mixed with fluid flowing out from the working medium side of the i-1 stage condenser and then flow through the i-1 stage throttle valve for throttling. The other flow from the i-th stage compressor 13 enters the i + 1-th stage compressor to be compressed.
The fourth step: and the other path of fluid flowing out of the nth-1 stage compressor enters the working medium side of an nth-stage heat regenerator 18 for cooling, then enters an nth-stage compressor 19 for compressing into superheated gas, the superheated gas flowing out of the nth-stage compressor 19 flows into the working medium side of an nth-stage condenser 17 for exchanging heat with the heat exchange fluid flowing out of the heat exchange fluid side of the nth-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 17 is divided into two paths, and one path of the fluid flows through the nth-stage bypass throttle valve 20 to be throttled and depressurized and is changed into a gas-liquid two-phase state. The throttled and depressurized gas-liquid two-phase fluid and the superheated gas flowing out of the nth-1 stage compressor exchange heat in the nth-stage heat regenerator 18, the exhaust temperature of the nth-1 stage compressor is reduced, and the gas-liquid two-phase fluid absorbs heat and evaporates into a saturated gas state. The other path of working medium flowing out from the working medium side of the nth-stage condenser 17 flows through the nth-stage throttle valve 10 to be throttled and decompressed, 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 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. The intermediate throttling incomplete cooling medium-high temperature heat pump system of the multi-stage compression multi-condenser is characterized in that i is more than or equal to 3 and less than or equal to n-1 in the system, and 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 condenser (4), the working medium side outlet of the first-stage compressor (3) is connected with the superheated gas side inlet of the second-stage heat regenerator (6), the superheated gas side outlet of the second-stage heat regenerator (6) is connected with the second-stage compressor (8), 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 throttle valve (11) is connected with the inlet of the first-stage throttle valve (5), the two-phase fluid side outlet of the second-stage heat regenerator (6) 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 (1), and the working medium side outlet; the working medium side outlet of the second-stage condenser (9) is connected with a second-stage heat regenerator (6) through a pipeline provided with a second-stage bypass throttle valve (7);
the outlet of the i-1 th stage compressor is connected with the inlet of the superheated gas side of the i-th stage regenerator (12), the outlet of the superheated gas side of the i-th stage regenerator (12) is connected with the inlet of the i-th stage compressor (13), the outlet of the i-th stage compressor (13) is connected with the inlet of the superheated gas side of the i +1 th stage regenerator, the outlet of the i-th stage compressor (13) is connected with the inlet of the working medium side of the i-th stage condenser (15), the outlet of the working medium side of the i-th stage condenser (15) is connected with the inlet of the i-th stage throttle valve (16), the outlet of the i + 1-th stage throttle valve is connected with the inlet of the i-th stage throttle valve (16), the outlet of the i-1-th stage throttle valve (16) is connected with the inlet of the i-1-th stage throttle valve; an outlet of a working medium side of the ith-stage condenser (15) is connected with an inlet of an ith-stage bypass throttle valve (14), an outlet of the ith-stage bypass throttle valve (14) is connected with a two-phase fluid side inlet of the ith-stage heat regenerator (12), and a two-phase fluid side outlet of the ith-stage heat regenerator (12) is connected with an inlet of an i-1-stage throttle valve;
the outlet of the nth-1 stage compressor is connected with the superheated gas side inlet of the nth stage heat regenerator (18), the superheated gas side outlet of the nth stage heat regenerator (18) is connected with the inlet of the nth stage compressor (19), the outlet of the nth stage compressor (19) is connected with the working medium side inlet of the nth stage condenser (17), the working medium side outlet of the nth stage condenser (17) is connected with the inlet of the nth stage throttle valve (10), and the outlet of the nth stage throttle valve (10) is connected with the inlet of the nth-1 stage throttle valve; an outlet of a working medium side of the nth-stage condenser (17) is connected with an inlet of an nth-stage bypass throttle valve (20), an outlet of the nth-stage bypass throttle valve (20) is connected with a two-phase fluid side inlet of an nth-stage heat regenerator (18), and a two-phase fluid side outlet of the nth-stage heat regenerator (18) is connected with an inlet of an n-1 st-stage throttle valve;
the normal-temperature water outlet is connected with the heat exchange fluid side inlet of the first-stage condenser (4), the heat exchange fluid side outlet of the first-stage condenser (4) is connected with the heat exchange fluid side inlet of the second-stage condenser (9), the heat exchange fluid side outlet of the second-stage condenser (9) is connected with the heat exchange fluid side inlet of the third-stage condenser, the heat exchange fluid side outlet of the ith-stage condenser (15) is connected with the heat exchange fluid side inlet of the (i + 1) th-stage condenser, the heat exchange fluid side inlet of the (n-1) th-stage condenser is connected with the heat exchange fluid side inlet of the nth-stage condenser (17), and the heat exchange fluid side outlet of the nth-stage condenser (17) is connected with the medium.
2. The intermediate throttle under-cooling medium-high temperature heat pump 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.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921465734.1U CN211119989U (en) | 2019-09-05 | 2019-09-05 | Multi-stage compression multi-condenser intermediate throttling incomplete cooling medium-high temperature heat pump system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921465734.1U CN211119989U (en) | 2019-09-05 | 2019-09-05 | Multi-stage compression multi-condenser intermediate throttling incomplete cooling medium-high temperature heat pump system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN211119989U true CN211119989U (en) | 2020-07-28 |
Family
ID=71695000
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201921465734.1U Expired - Fee Related CN211119989U (en) | 2019-09-05 | 2019-09-05 | Multi-stage compression multi-condenser intermediate throttling incomplete cooling medium-high temperature heat pump system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN211119989U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112325509A (en) * | 2020-10-28 | 2021-02-05 | 青岛理工大学 | Intercooling heat recovery trigeminy supplies heat pump system |
-
2019
- 2019-09-05 CN CN201921465734.1U patent/CN211119989U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112325509A (en) * | 2020-10-28 | 2021-02-05 | 青岛理工大学 | Intercooling heat recovery trigeminy supplies heat pump system |
| CN112325509B (en) * | 2020-10-28 | 2023-06-27 | 青岛理工大学 | Intermediate cooling heat recovery triple heat supply pump system |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN210569370U (en) | Low-temperature frequency conversion air source heat pump unit | |
| CN109708337B (en) | Multistage series compression heat pump unit | |
| CN110986414B (en) | Multi-temperature-zone and large-temperature-span heat pump circulating system adopting ejector for increasing efficiency | |
| CN112229085B (en) | Low-temperature heat pump circulating system and circulating method suitable for large temperature span | |
| CN108318273B (en) | Multicycle heat pump experiment table | |
| WO2014185525A1 (en) | Energy conversion system | |
| CN111141054B (en) | Transcritical two-stage supercooling injection carbon dioxide system and application | |
| CN215062959U (en) | Frequency conversion overlapping type air source heat pump system | |
| CN110736262A (en) | injection supercharging two-stage supercooling transcritical CO2Dual temperature system and application | |
| CN211119989U (en) | Multi-stage compression multi-condenser intermediate throttling incomplete cooling medium-high temperature heat pump system | |
| CN110500876B (en) | Multistage compression multi-condenser intermediate complete cooling heat pump drying system | |
| CN112963979A (en) | Overlapping heat pump system capable of realizing work cycle conversion | |
| CN110513902B (en) | Multi-stage evaporation condensation mechanical supercooling transcritical CO 2 Middle-high temperature heat pump system | |
| CN110307669B (en) | Solar energy synergy multi-mode heating device based on compression heat pump circulation | |
| CN211120563U (en) | Multi-stage compression multi-condenser intermediate complete cooling heat pump drying system | |
| CN111288675A (en) | Mixed working medium refrigerating system and air conditioner | |
| CN111141051B (en) | Absorption compression injection composite cascade supercooling transcritical CO 2 Cold and hot combined supply system | |
| CN211119988U (en) | Multistage compression multistage condensation intermediate flash incomplete cooling medium-high temperature heat pump system | |
| CN210861771U (en) | Multistage evaporation and condensation mechanical supercooling transcritical CO2 medium-high temperature heat pump system | |
| CN210861299U (en) | Thermoelectric super-cooling trans-critical CO2Heat pump combined heating system | |
| CN210165624U (en) | A multistage condensing system for vapor recovery system | |
| CN210004626U (en) | ground source heat pump heat recovery unit with high-efficiency throttling system | |
| CN110296625B (en) | Parallel-type cold-heat-electricity three-cogeneration Kazakh circulating system | |
| CN211060434U (en) | Injection supercharging two-stage supercooling transcritical CO2Dual temperature system | |
| CN112033038A (en) | Air source heat pump drying system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20200728 Termination date: 20210905 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |