CN110520683A - Heat pump and method for running heat pump - Google Patents
Heat pump and method for running heat pump Download PDFInfo
- Publication number
- CN110520683A CN110520683A CN201880022852.7A CN201880022852A CN110520683A CN 110520683 A CN110520683 A CN 110520683A CN 201880022852 A CN201880022852 A CN 201880022852A CN 110520683 A CN110520683 A CN 110520683A
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- China
- Prior art keywords
- fluid
- bypass line
- heat pump
- subflow
- evaporator
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B30/00—Heat pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/06—Superheaters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0403—Refrigeration circuit bypassing means for the condenser
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/23—Time delays
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2501—Bypass valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2509—Economiser valves
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
- Filling Or Discharging Of Gas Storage Vessels (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The present invention relates to a kind of heat pump (12,26), and with fluid circuit (21,28), the fluid circuit includes at least one evaporator (10)；Followed downstream by compressor unit (7)；At least one followed downstream by liquefier (8)；With followed downstream by expansion cell (9)；With the first bypass line (42), it has at least one by-passing valve (43), and the fluid circuit in compressor unit (7) downstream and in the liquefier (8) upstream is connect with the fluid in evaporator (10) downstream and in compressor unit (7) upstream.Heat pump has the region of operation at part load extended towards lower power of heat source.For this purpose, heat pump includes the second bypass line (45) with the mechanism (46) for carrying out dosage to flow, wherein can be imported the liquid phase of fluid in the first bypass line (42) by means of the second bypass line.
Description
Technical field
The present invention relates to a kind of heat pumps, and with fluid circuit, circulation has working fluid in the fluid circuit.Fluid
Circuit includes: at least one evaporator, is used to the thermal energy of heat source being transferred to fluid；Followed downstream by compressor list
Member is used for compression fluid；At least one followed downstream by liquefier, be used to for the thermal energy of fluid being released in specific heat
It is heat sink in the higher temperature level of source；With followed downstream by expansion cell, be used for the expansion of fluid.Heat pump further includes first
Bypass line has at least one by-passing valve, enables fluid circuit in compressor unit downstream and in liquefier upstream
Enough fluids with trip under the vaporizers and in compressor unit upstream are connect.
The invention further relates to a kind of methods for running heat pump, wherein fluid is continuously guided simultaneously in fluid circuit
And herein by thermal energy from heat source to evaporator in fluid on, wherein fluid is at least partly evaporated, and by fluid
Then compression.Then by fluid in order to by thermal energy be released in than heat source higher temperature level on it is heat sink and at least partly
Liquefaction, and subsequent to cool down and expand, wherein after being compressed and liquefying in the operation at part load of fluid circuit
The first subflow of fluid is separated via the first bypass line before and swims and is conveyed to again before the compression under the vaporizers
Fluid circuit.
Background technique
By evaporative fluid by thermal energy in heat pump, that is to say, that heat absorbed by heat source and be released to it is heat sink, wherein
The fluid recycles in the fluid circuit of heat pump along operative orientation.Here, will have the fluid of the thermal energy absorbed by means of pressure
Contracting machine reaches the stress level of raising and then liquefies under the condensing temperature improved relative to evaporating temperature.In order to by fluid
It is returned in original state at the end of circulation, makes its expansion, thus its temperature reduces again.
The efficiency of heat pump is by means of the coefficient of performance (English Coefficient of Performance；COP it) measures, wherein
The inverse of efficiency of the coefficient of performance under best-case through carnot's cycle process provides.The coefficient of performance corresponds to income and expends
Quotient.If heat pump is used to heat it is heat sink, this correspond to is released to heat sink heat QwarmDivided by the acting of compressor
Consume Wmech.Numerical difference between the evaporating temperature and condensing temperature of fluid is bigger (temperature rising), and the efficiency of heat pump is lower.
It is desirable that the quality stream of heat pump, temperature levels and time availability are approximately constants, so as to be attributed to heat
The efficiency remained unchanged and power of pump.If heat pump run by means of the waste heat from industrial process, this can occur
The fluctuation of three parameters.In these cases, when parameter reduces, heat pump must be with operation at part load, so as to as far as possible
Utilize the heat as much as possible of heat source.In the period with reduced power of heat source, the reduction for the fluid being evaporated
Volume flow is flowed out from evaporator.If the compressor unit of heat pump includes the piston compressor or screw rod according to extrusion principle
Formula compressor, then this heat pump of the prior art is for example matched by matching the revolving speed of compressor in operation at part load
In the volume flow of the reduction for the fluid being evaporated.Whirlpool is generally included for using the heat pump of the waste heat in industrial process
Wheel compression machine is as the compressor mechanical according to flow principles.The operation of turbo-compressor is by means of the revolving speed tune that is carried out with frequency converter
The matching of the volume flow of the reduction to the gaseous fluid flowed out from evaporator is saved only in the partial load region of restriction (up to body
The about 90%) interior of product stream is possible.If revolving speed continues to reduce, it would be possible that cause turbo-compressor on the pressure side on
Stream destruction and cause so-called pumping procedure at turbo-compressor.This will be avoided by, so that the volume flow is not low
In minimum volume stream relevant to the operating point of compressor.In order to by the Operating match of turbo-compressor in being flowed out from evaporator
Reduction volume flow it is also known that, turbo-compressor is equipped with the adjustable angle of attack of air-intake guide vane (IGV).Pass through
Adjust air-intake guide vane, in the case where pressure ratio remains unchanged can by volume flow throttle until volume flow about
70%.It is also known that in order to which the volume flow by the Operating match of heat pump in the reduction of the fluid flowed out from evaporator is arranged
Bypass line at least one by-passing valve so that compressor unit downstream and liquefier upstream fluid circuit with
Evaporator downstream and fluid circuit in compressor unit upstream can fluidly connect.It can be set by means of by-passing valve and flow through pressure
The volume flow of contracting machine unit.However, also improving intake-gas (in compressor unit by the subflow flowed via bypass line
Into the fluid in region) temperature so that also improve the temperature of pressed gas (in the fluid of the output of compressor unit)
Degree.Not only for fluid itself (due to being higher than the thermal decomposition of critical-temperature) and there is temperature for compressor material (thermal stress)
Spend the upper limit.The temperature upper limit can be different according to fluid and material, the lower temperature limiting in two of them temperature
The share for flowing through bypass line of fluid stream also limits the operation at part load towards lower power of heat source direction of heat pump in turn
Region.
Summary of the invention
The present invention is based on purpose be to propose a kind of heat pump for being initially mentioned type and a kind of for running this heat pump
Method, wherein heat pump has the region towards lower power of heat source Directional Extension of operation at part load.
The purpose is accomplished in that including having for carrying out to flow in the heat pump for being initially mentioned type
Second bypass line of the mechanism of dosage, wherein the liquid phase of fluid can be imported the first bypass pipe by means of the second bypass line
It swims in road and/or under the vaporizers and is imported in fluid circuit in compressor unit upstream.
Heat pump according to the present invention is constituted for using in the method according to the invention.In the operation at part load of heat pump
In, it mixes via the fluid that the second bypass line flows with the fluid flowed via the first bypass line and evaporates herein.It is logical
It crosses blended liquid phase and the temperature of the first subflow is reduced to lower mixing temperature from pressed gas temperature.Via the second bypass line
The second subflow separated is evaporated by means of the first subflow according to the present invention, without using heat source thus, wherein described second
Subflow has been imported into evaporator originally in the case where not being separated out.It is preferred that being mixed in the first bypass line, side
Formula is: the second bypass line is passed through in the first bypass line.The mixing however can also swim under the vaporizers and compressor
Carry out within the fluid circuit of unit upstream, mode is: the two bypass lines are passed through in fluid circuit in this region
And these subflows are mixed with each other before entering in compressor unit at that.It is swum under the vaporizers in fluid circuit via detour
Extend to compressor and provide in region of the fluid circuit for the mixing of the two subflows it is accordingly long apart from when, institute
The variations for stating alternative are especially suitable for.
The two bypass lines are directed to operation at part load, in the case where the first bypass line simultaneously including at least one valve
It and include mechanism for carrying out dosage to flow in the case where the second bypass line.For the flow to the second bypass line
The mechanism for carrying out dosage for example can be pump and/or valve.It is can setting and/or controllable and/or adjustable that valve or pump can be
Section and for example can by include heat pump heat pump facility control/regulating device manipulate and/or adjust.
The ratio of volume flow and volume flow to each other can be selected as relative to each other in the operation at part load of heat pump,
So that fluid when compressing beginning, is at least saturated vapor shape during compression and at the end of compression, until by excessively adding
Heat.This is avoided the hydraulic shock using turbo-compressor at compressor.Volume flow and ratio to each other can
To be selected as relative to each other in the operation at part load of heat pump, so that being no more than material or gas correlation at the end of compression
Maximum temperature.This avoid fluid decomposition and prevent due to temperature it is excessively high caused by compressor unit material damage
It is bad.By the constituted mode according to the present invention of heat pump, heat pump can be in operation at part load by means of higher volume flow
It runs and then is particularly suitable for extending the partial load region in the heat pump at least one turbo-compressor.In turbine pressure
In contracting machine, it should be noted that the sufficiently high volume flow at the corresponding operating point of turbo-compressor, the volume flow not lower than with
The relevant minimum volume stream in operating point, so that the stream on the pressure side towards compressor is not destroyed.If heat pump is by means of heat source
Operation, power fluctuate widely and temporarily can be using especially small values, then setting according to one embodiment of present invention
There is control/adjusting unit, the control/adjusting unit is in operation at part load to the volume flow for passing through bypass line and two
The ratio of subflow to each other is set and is monitored, so that being no more than material or gas relevant maximum temperature at the end of compression
And heat pump is cut off when power of heat source is too small.According to another embodiment of the present invention, in the operation at part load of heat pump
The revolving speed of these and compressor sets and/or controls and/or regulates to carry out in combination.In turbo-compressor can as an alternative or
It is additionally carried out and the setting of the angle of attack of guide vane and/or the combination controlled and/or regulated.
Advantageous design scheme of the invention below with provided in dependent claims, feature can individually and with
The form application of any combination each other.
It can advantageously be proposed in heat pump according to the present invention, compressor unit includes at least one compressor, wherein
Compressor is turbo-compressor.
The design scheme of the invention is particularly suitable for the heat in the industrial application in the power bracket greater than 500kW
Pump.According to the present invention, it can be realized compared with the existing technology in the operation at part load of heat pump stronger by bypass line
Volume flow so that in the lower Shi Caike of power of heat source in the heat pump according to the present invention at least one turbo-compressor
No longer to maintain the relevant minimum volume stream in operating point.
It can advantageously be proposed in heat pump according to the present invention, expansion cell includes the expansion of at least two series connections
Equipment, wherein the separator for separated gas phase and liquid phase is connected between the two bloating plants, wherein the second bypass pipe
The composition of road and separator is connected for collecting the regional fluid of liquid phase.
Bloating plant can be throttle valve.Throttle valve has the contraction flow region of flow path, so that the section shunk in percolation
Period fluid is expanded since pressure reduces.The cross section of throttle valve can be and can set.Between the two bloating plants
The separator of setting is used to improve the efficiency of heat pump, and mode is: isolated gas phase at least portion between two compression steps
It is conveyed to fluid circuit with dividing.According to design scheme according to the present invention, the composition of the second bypass line and separator is for receiving
Collect the regional fluid connection of liquid phase.Separator may include the pressure vessel for separated gas phase and liquid phase.In pressure vessel,
The gas phase that fluid is collected in upper area, wherein gaseous fluid can be via intake line by least one in this region
A compressor sucking.Second bypass line can for example be separated from the lower area of pressure vessel.
Another advantageous design scheme of the invention can propose, the second bypass line and evaporator are flooded in operation
Regional fluid connection not.
The design scheme of the invention is also suitable for the heat pump without separator.
Advantageously, it can also propose, heat pump includes the mechanism for excessively heating the fluid flowed out from evaporator, described
Mechanism has heat exchanger, and the heat exchanger is configured to so that its by from it is being flowed out in liquefier, in entering expansion cell
Fluid before is thermally connected with from fluid flow out in evaporator, before entering in compressor unit, wherein the first bypass
Pipeline is passed through in fluid circuit in heat exchanger downstream and the second bypass line is passed through in the first bypass line or equally exists
Heat exchanger downstream is passed through in fluid circuit.
The design scheme of the invention realizes the high temperature fluid with the positive slope of the freezing curve in tephigram
It uses.In order to which (not only under full load but also at part load) does not reach the following state model of fluid during compression fluid
In enclosing, the formation drop in compressor unit is caused in turn result in the damage due to caused by dropping liquid impact in the state range
Bad, fluid must be heated excessively before entering in compressor housing.The degree excessively heated can be by means of heat exchanger
Area be directed to full load operating energy loss.The two bypass lines for example can be passed through fluid in the output area of heat exchanger
In circuit.For the startup stage of operation of heat pump, heat source can be connected with external energy supply device, the energy supply device
It is arranged and constitutes the fluid in the fluid circuit for transferring heat to heat exchanger downstream and compressor unit upstream.
It is another object of the present invention to propose a kind of method for running heat pump for being initially mentioned type, by means of institute
The method of stating can be realized the region towards lower power of heat source Directional Extension of operation at part load.
The purpose is real in the following way in the method for running heat pump for being initially mentioned type according to the present invention
It is existing: swim after partial liquefaction and on an evaporator from fluid circuit via the second bypass line separate liquid subflow and
It is mixed before compression with the first subflow.
In the operation at part load of heat pump, by the fluid flowed via the second bypass line and via the first bypass line
The fluid of flowing is mixed and is evaporated herein.By blended liquid phase by the temperature of the first subflow from pressed gas temperature be reduced to compared with
Low mixing temperature.The second subflow separated via the second bypass line is evaporated by means of the first subflow according to the present invention, and
Heat source need not be used thus, wherein second subflow has been imported into evaporator originally in the case where not being separated out.It is preferred that
It is mixed in the first bypass line.For this purpose, the subflow of liquid is imported in the first bypass line, mode is: for example
Second bypass line is passed through in the first bypass line.It is described mixing however can also additionally or alternatively swim under the vaporizers and
Carry out within fluid circuit before compression fluid, mode is: the subflow of liquid is additionally or alternatively in evaporator
In downstream and before the compression importing fluid circuit, such as its mode is: the second bypass line is additionally or alternatively at this
It is passed through in fluid circuit in region.
By the composition scheme according to the present invention of method, heat pump can be in operation at part load with higher volume flow
Operation is to be particularly suitable for extending the partial load region in the heat pump at least one turbo-compressor.In turbine pressure
In contracting machine, it should be noted that the sufficiently high volume flow at the corresponding operating point of turbo-compressor, the volume flow not lower than with
The relevant minimum volume stream in operating point, to not destroy the stream on the pressure side towards compressor.
Can also be considered as advantageously, in the operation at part load of heat pump, the ratio setting of the first and second subflows and/
Or it controls and/or regulates as so that fluid when compressing beginning, is at least saturated vapor during compression and at the end of compression
Shape, until being heated excessively.
The design scheme of the invention especially prevents in the heat pump at least one turbo-compressor due to pressing
It is damaged caused by liquid in contracting machine.In order to be set in operation at part load to the ratio of the first and second subflows
And/or control and/or regulate, at least one valve can be equipped in the case where the first bypass line and in the second bypass line
In the case where the mechanism that can be equipped with for carrying out dosage to flow for example pump and/or valve.Valve or pump can be can set and/
Or it is controllable and/or adjustable and for example can manipulate and/or adjust by means of control/regulating device.Volume flow is set
It is fixed and/or control and/or regulate with the revolving speed of compressor can set and/or control according to one embodiment of present invention and/
Or it adjusts and carries out in combination.Turbo-compressor can be additionally carried out the setting with the angle of attack of guide vane according to the present embodiment
And/or the combination controlled and/or regulated.
It can also be considered as advantageously, setting the ratio of the first and second subflows in the operation at part load of heat pump
And/or it controls and/or regulates as so that being no more than material correlation or gas relevant maximum temperature at the end of compression.
The design scheme of the invention is suitable for the operation with the heat pump of heat source, and the power of the heat source is significantly
It fluctuates and needs the operation of heat pump in the limit range of the range of operation in heat pump.The anti-fluid stopping of design scheme
Body decomposes and the material damage due to caused by excessive temperature at least one compressor for compression.
Advantageously, it can also propose, the volume flow of the first and second subflows is set and/or controlled in operation at part load
It makes and/or is adjusted to, so that being not less than minimum volume stream relevant to the operating point of compressor.
The design scheme of the invention is particularly suitable for using the heat pump at least one turbo-compressor for holding
Row method.
Can also be considered as advantageously, the subflow of liquid is imported in the first bypass line and/or under the vaporizers trip and
It imports in fluid circuit before the compression.
The design scheme of the invention can be realized the two subflows mixed within the first bypass line and/or
It evaporator downstream and is mixed within fluid circuit before the compression.
The mixing preferably carries out within the first bypass line.For this purpose, the subflow of liquid can import the first bypass pipe
Lu Zhong, mode are: for example the second bypass line is passed through in the first bypass line.It is described mixing however can also additionally or
It swims and is carried out within fluid circuit before compression fluid under the vaporizers as an alternative, mode is: the subflow of liquid is attached
Add ground or swim and imported in fluid circuit before the compression under the vaporizers as an alternative, such as its mode is: the second bypass pipe
Road is additionally or alternatively passed through in fluid circuit in this region.
Another advantageous design scheme of the invention can propose that heat pump is run by high temperature fluid, the high temperature fluid
Freezing curve substantially there is positive slope in tephigram, and by the thermal energy of the fluid circuit after liquefaction and swollen
Be transferred to before swollen on evaporator downstream and fluid before the compression so that fluid compress start when, during compression with
It is heated excessively after being compressed, wherein transmitting the two subflows by the first subflow or as an alternative in operation at part load
Fluid circuit is conveyed to after thermal energy.
Advantageous design scheme of the invention can be realized the operation by means of high temperature fluid of heat pump, the high temperature fluid
This slope with freezing curve must be heated excessively to avoid the damage at compressor before the compression in turn.Thermal energy
Transmission can be carried out by means of heat exchanger.The degree excessively heated can be set by the design of the area of heat exchanger.
For example, the heat exchanger can choose as so that not only fluid is after being compressed under full load but also at part load
In abiding by, there are in the state of safe spacing (temperature difference) with freezing curve.
It can also advantageously propose, expansion carries out at least two expansion steps, wherein at least in two expansion steps
Between separated by the liquid phase separation of the gas phase of fluid and fluid, and by the subflow of liquid from liquid phase.
The separation of the gas phase and liquid phase that carry out between two expansion steps exists for improving the efficiency of heat pump, mode
In: isolated gas phase is at least partly conveyed to fluid circuit between two compression steps.According to design according to the present invention
Scheme is separated via the second bypass line as the second subflow to isolated liquid phase part, wherein the liquid phase is otherwise all
It is conveyed to evaporator.
Also it can be considered advantageously, the subflow of liquid is separated from the region of evaporator being submerged.
The design scheme of the invention is also suitable for the operation of the heat pump without separator.
Detailed description of the invention
Other suitable design schemes of the invention and advantage are theme of the embodiment of the present invention referring to the explanation of attached drawing,
Wherein identical appended drawing reference has indicated the component of phase same-action.
It is shown here:
Fig. 1 shows the schematic diagram of the fluid circuit of heat pump according to prior art；
Fig. 2 shows the schematic diagram of the tephigram of fluid R134a, there is shown with it is shown in FIG. 1 according to prior art
Condition curve during the fluid circulation of heat pump；
Fig. 3 shows the schematic diagram of the tephigram of fluid, and wherein freezing curve has substantially positive slope and shows stream
Condition curve of the body when flowing the fluid circuit of heat pump according to prior art shown in Fig. 1；
Fig. 4 shows the schematic diagram of the fluid circuit of the heat pump of first embodiment according to the present invention；And
Fig. 5 shows the schematic diagram of the flow chart of the method for third embodiment according to the present invention.
Specific embodiment
Fig. 1 schematically illustrates the fluid circuit 21 of heat pump 12 according to prior art.Fluid 2 passes through on flow direction 11
Heat pump 12 conveys.The evaporative fluid in the case where absorbing the thermal energy of heat source 4 of evaporator 10, so that it occupies evaporating state 1.Institute
It states in evaporating state 1, fluid 2 enters in compressor unit 7, and the compressor unit includes compressor 7a, and fluid is pressed
It is reduced to compressive state 3.The fluid described in compressive state 3 flows into liquefier 8 in the case where thermal energy is released to heat sink 20
And it is converted in condensing state 5 and is finally expanded in expansion cell 9 by means of bloating plant 9a.Fluid 2 uses as a result,
Swelling state 6, wherein fluid is fed to evaporator 10 in this state again.Therefore, fluid connects during the operation of heat pump 12
Continuously conveyed according to flow direction 11 by heat pump 12 and absorbed when evaporating in the vaporizer 10 herein heat source 4 heat and
Thermal energy is released to heat sink 20 on the higher temperature levels of temperature levels than heat source 4 during liquefying in liquefier 8.
Fig. 2 shows tephigram 23, the tephigram according to plotting planes to the right, i.e., entropy 14 is shown on axis of abscissas and
On plotting planes upwards, i.e., temperature 13 is shown on axis of ordinates.Tephigram 23 shows freezing curve 18, the liquidus of fluid
19 and different coherent conditions.Freezing curve 18 separates gas phase 15 and two-phase section 16, wherein in two-phase section 16 fluid with
Liquid, and also exist with gaseous state.Liquidus 19 separates two-phase section 16 and liquid phase 17.The tephigram 23 shown is shown
The freezing curve 18 with substantially negative slope of fluid.
It is equally schematically illustrated in Fig. 2, fluid is in the fluid time for passing through heat pump according to prior art shown in Fig. 1
Used different thermodynamic (al) state when road.It is originated from evaporating state 1, compression is reached by compression according to flow direction 11
State 3.Compressive state 3 is located within gas phase 15, and thus compressor 7a will not be sent out in the design scheme as turbo-compressor
It is raw due to form hydraulic shock caused by drop in a fluid and caused by damage.The connection shown between each state
Line is used as the connecting line of straight line to show in figure 2 and figure 3, however can also be different from the ideal stretching, extension.From compressive state 3
Starting sets condensing state 5 by liquefier 8, and the condensing state is on liquidus.It is originated from condensing state 5, due to
Fluid passes through bloating plant 9a and reaches swelling state 6 and then reach fluid again by energy input in the vaporizer 10
Evaporating state 1.The circuit of heat pump 12 is closure as a result,.
Fig. 3 similarly shows tephigram 24 with Fig. 2, however belongs to another fluid.It is the liquidus 19 of fluid and cold
The trend of solidifying curve 18 defines two-phase section 16 very outstanding, so that freezing curve 18 substantially has positive slope.If this
Kind fluid is subjected to the fluid circulation of heat pump according to prior art shown in FIG. 1, then compressive state 3 is located at two-phase section 16
Within.Accordingly, will cause in the case where turbo-compressor in compressor 7a as hydraulic shock and caused by damage.
Fig. 4 shows the fluid circuit 28 for schematically illustrating the heat pump 26 of first embodiment according to the present invention.It is returned in fluid
With being provided with tool everywhere, there are two the compressor units 7 of compressor 7a, 7b on evaporator 10 for streamwise in road 28.Compression
Machine 7a and 7b are arranged in series and are configured to turbo-compressor.In 7 downstream of compressor unit, fluid circuit 28 includes liquefaction
There are two the expansion cells 9 of bloating plant 9a, 9b for being arranged in series for device 8 and subsequent tool.Bloating plant 9a and/or 9b can be with structures
As throttle valve or for example it is configured to expansion valve.The fluid circuit 28 of heat pump 26 further includes for flowing out to from evaporator 10
The mechanism 34 that fluid excessively heats, the mechanism have heat exchanger 32.Heat exchanger 32 is configured to, so that it will be from liquefier
It is being flowed out in 8, enter expansion cell 9 in front of fluid with from it is being flowed out in evaporator 10, enter compressor unit 7 in
Fluid before is thermally connected.Additionally, the separator 30 for separated gas phase and liquid phase is connected to two bloating plants 9a and 9b
Between, there is the gas phase intake line 36 being passed through in fluid circuit 28 between two compressors 7a and 7b.In order in starting rank
Guarantee that, to the sufficiently over heating of the fluid flowed out from evaporator 10, mechanism 34 additionally includes accessible heating during section
Equipment 38, the heating equipment can be heated by means of external energy source 40.For operation at part load, heat pump 26 is wrapped
The first bypass line 42 and the second bypass line 45 are included, first bypass line has by-passing valve 43, so that in compressor list
First 7 downstreams and fluid circuit 28 in 8 upstream of liquefier are returned with the fluid in 10 downstream of evaporator and in 7 upstream of compressor unit
Road 28 fluidly connects.Second bypass line includes the mechanism 46 for carrying out dosage to flow, and the mechanism is configured to valve 47.The
Two bypass lines 45 are separated from separator 30 and are passed through in the first bypass line 42, so that can by means of the second bypass line 45
The liquid phase separated in the slave separator 30 of fluid is imported in the first bypass line 42.
As an alternative, the second bypass line 45 substitution separator can also be separated from the region 49 being submerged.Second bypass pipe
The stretching, extension of the alternative on road is not shown in the accompanying drawings.
In operation at part load via these bypass lines flowing subflow ratio can by means of valve for pair
It is set and/or controls and/or regulates under the mechanism of flow progress dosage as so that fluid (evaporating state when compressing beginning
1b), during compression (compressive state 3a and 3b) and (compressive state 3c) is at least the straight of saturated vapor shape at the end of compression
To being heated excessively and (compressive state 3c) is no more than that material is relevant or the relevant maximum temperature of gas at the end of compression.
Different from fluid circuit shown in Fig. 1, heat pump 26 according to the present invention can be realized heat pump in lower heat source
Operation under power.Additionally, the embodiment shown, which can be realized, combines high performance using the positive slope with freezing curve
The high temperature fluid of coefficient.
Fig. 5 schematically illustrates embodiment according to the method for the present invention with process, wherein in the method step being prepared
Following fluid is selected and applied in rapid VS1 in order to run heat pump, the fluid is in pressure-enthalpy chart with substantially positive slope
Freezing curve.
The excessive heating of fluid of the selection in fluid circuit in the method and step VS2 being prepared, such as by means of
The design of heat exchange area, so that the spacing with the freezing curve at compressor endpoint is at least 10K, especially 10K to 20K.
The data for being used for operation at part load are consigned into control/adjusting unit in the method and step VS3 being prepared,
The especially described data abide by the maximum temperature of pressed gas and the data abide by the operating point correlation in compressor unit
Minimum volume stream.
In method and step VS4, heating is accessed in the startup stage of the operation of the heat pump for excessively heating to fluid
Equipment.In method and step VS5, by thermal energy from heat source to evaporator in fluid on, wherein fluid at least partly evaporates.
In method and step VS6, the excessively heating after transporting heat energy and before the compression by fluid, and liquefier will be left herein
The thermal energy of fluid extract and be transferred on the fluid for leaving evaporator before the compression before inflation.
In method and step VS7, then fluid is compressed in the first compression step.
Compressed fluid is compressed in the second compression step in method and step VS8.
Fluid is at least partly liquefied in method and step VS9, thermal energy is released in than heat source higher temperature
It is heat sink in level.Fluid is expanded in the first expansion step in order to cooling in method and step VS10.In method and step
In VS11 by the gas phase of fluid and the liquid phase separation of fluid and by gaseous fluid between at least two compression steps at least portion
It is conveyed to fluid with dividing.In method and step V12, fluid is expanded in the second expansion step, and be conveyed to evaporation again
The device and fluid recycled in the fluid circuit of heat pump is consecutively carried out method and step VS5 to VS12.If heat pump is in part
It is run in load operation, then additionally continuously repeating method and step VS13 and VS14.In method and step VS13, in compression
The first subflow of fluid is separated afterwards and via the first bypass line from fluid circuit before liquefaction and is swum under the vaporizers
It is conveyed to fluid circuit again before the compression and swims after partial liquefaction and on an evaporator from fluid circuit via
Second subflow of liquid is separated and is mixed with the first subflow by two bypass lines.In addition, with current in evaporating state 1a
Volume flow, the Current Temperatures in compressive state 3c and the current volume flow in evaporating state 1b relatively, will be via
The volume flow of two bypass lines and its proportion adjustment to each other at so that fluid compress start when, during compression and
At the end of compression be at least saturated vapor shape until be heated excessively and at the end of compression be no more than maximum temperature simultaneously
And it is not less than minimum volume stream relevant to the operating point of compressor.It checks in method and step VS14: whether can currently abide by
Keep all conditions of method and step VS13.If it is not, so in method and step VS15 that heat pump is too small due to heat source
Power and cut off.If it is then repetition methods step V13.
Claims (13)
1. a kind of heat pump (12,26), with fluid circuit (21,28), the fluid circuit includes at least one evaporator
(10), it is used to the thermal energy of heat source (4) being transferred to fluid (2)；Followed downstream by compressor unit (7), be used to press
Contracting fluid；At least one followed downstream by liquefier (8), be used to for the thermal energy of the fluid being released in than the heat
Heat sink (20) in source (4) higher temperature level；With followed downstream by expansion cell (9), be used for the expansion of the fluid；
With the first bypass line (42), there is at least one by-passing valve (43), so that in the compressor unit (7) downstream and in institute
State liquefier (8) upstream fluid circuit can in the evaporator (10) downstream and in the compressor unit (7) upstream
Fluid connection,
It is characterized in that,
With the second bypass line (45), second bypass line has the mechanism (46) for carrying out dosage to flow,
In the liquid phase of the fluid can be imported in first bypass line (42) by means of second bypass line and/or
It the evaporator downstream and is imported in the fluid circuit in the compressor unit (7) upstream.
2. heat pump (12,26) according to claim 1,
It is characterized in that,
The compressor unit (7) includes at least one compressor (7a, 7b), wherein the compressor (7a, 7b) is turbine pressure
Contracting machine.
3. heat pump (12,26) according to claim 1 or 2,
It is characterized in that,
The expansion cell (9) includes the bloating plant (9a, 9b) of at least two series connections, wherein in two bloating plants
The separator (30) for separated gas phase and liquid phase is connected between (9a, 9b), wherein second bypass line (45) and institute
The composition for stating separator (30) is connected for collecting the regional fluid of the liquid phase.
4. heat pump (12,26) according to claim 1 or 2,
It is characterized in that,
Second bypass line (45) and the region (49) of the evaporator being submerged in operation fluidly connect.
5. heat pump (12,26) according to any one of claim 1 to 4,
It is characterized in that,
The heat pump includes the mechanism (34) that the fluid (2) for will flow out from the evaporator excessively heats, the mechanism tool
Have heat exchanger (32), the heat exchanger is configured to so that it is that it will be flowed out from the liquefier (8), described in the entrance
Fluid before in expansion cell (9) with it is being flowed out from the evaporator (10), in entering the compressor unit (7) it
Preceding fluid is thermally connected, wherein first bypass line (42) is passed through the fluid circuit in the heat exchanger (32) downstream
(28) in and second bypass line (45) is passed through in first bypass line or equally under the heat exchanger
Trip is passed through in the fluid circuit.
6. a kind of method for running heat pump, wherein by fluid continuously in fluid circuit guidance and herein by thermal energy from
Heat source is on the fluid into evaporator, wherein the fluid is at least partly evaporated (VS5), and by the fluid with
Compress (VS7, VS8) afterwards, and subsequent to thermal energy is released in than heat sink in heat source higher temperature level and
The fluid is at least partly liquefied (VS9), and subsequent to it is cooling and by the fluid expansion (VS10, V12), and
In the operation at part load of the fluid circuit after being compressed and before liquefaction by the first subflow of the fluid via
First bypass line separates and is conveyed to again in the evaporator downstream and before the compression the fluid circuit,
It is characterized in that,
Via second after partly liquefying and in the vaporizer upstream in the operation at part load of the fluid circuit
Second subflow of liquid is separated and is mixed before the compression with first subflow by bypass line.
7. according to the method described in claim 6,
It is characterized in that,
The ratio of first subflow and the second subflow is set and/or is controlled and/or regulated as so that the fluid is compressing
When beginning, saturated vapor shape is at least during compression and at the end of compression, until being heated excessively.
8. method according to claim 6 or 7,
It is characterized in that,
The ratio of first subflow and the second subflow is set and/or is controlled and/or regulated as so that at the end of compression not
Or gas relevant maximum temperature relevant more than material.
9. the method according to any one of claim 6 to 8,
It is characterized in that,
By the volume flow of first subflow and the second subflow set and/or control and/or regulate for so that not less than with it is described
The relevant minimum volume stream in the operating point of compressor.
10. method according to claim 6 or 9,
It is characterized in that,
The subflow of liquid is imported in first bypass line (42) and/or in the evaporator (10) downstream and in compression
It is preceding to import in the fluid circuit.
11. the method according to any one of claim 6 to 10,
It is characterized in that,
The heat pump (12,26) is run by means of high temperature fluid, the freezing curve (18) of the high temperature fluid tephigram (23,
24) substantially there is positive slope in, and the thermal energy of the fluid circuit is transferred to institute after liquefaction and before inflation
State on evaporator downstream and fluid before the compression so that the fluid compress start when, during compression and compressing
It is heated excessively (VS6) later, wherein passing two subflows by first subflow or as an alternative in operation at part load
The fluid circuit is conveyed to after defeated thermal energy.
12. the method according to any one of claim 6 to 11,
It is characterized in that,
Expanded at least two expansion steps, wherein at least between two expansion steps by the gas phase of the fluid with
The liquid phase separation (VS11) of the fluid, and the subflow of liquid is separated from liquid phase.
13. the method according to any one of claim 6 to 11,
It is characterized in that,
The subflow of liquid is separated from the region of the evaporator being submerged.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102017205484.0A DE102017205484A1 (en) | 2017-03-31 | 2017-03-31 | Heat pump and method for operating a heat pump |
| DE102017205484.0 | 2017-03-31 | ||
| PCT/EP2018/057956 WO2018178169A1 (en) | 2017-03-31 | 2018-03-28 | Heat pump and method for operating a heat pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110520683A true CN110520683A (en) | 2019-11-29 |
| CN110520683B CN110520683B (en) | 2021-12-21 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201880022852.7A Active CN110520683B (en) | 2017-03-31 | 2018-03-28 | Heat pump and method for operating a heat pump |
Country Status (7)
| Country | Link |
|---|---|
| EP (1) | EP3583365B1 (en) |
| JP (1) | JP7074969B2 (en) |
| KR (1) | KR102344187B1 (en) |
| CN (1) | CN110520683B (en) |
| DE (1) | DE102017205484A1 (en) |
| DK (1) | DK3583365T3 (en) |
| WO (1) | WO2018178169A1 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102020130063A1 (en) | 2020-11-13 | 2022-05-19 | CTS Clima Temperatur Systeme GmbH | Temperature control system and method for operating a temperature control system |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101512247A (en) * | 2006-09-11 | 2009-08-19 | 大金工业株式会社 | Refrigeration device |
| CN102388279B (en) * | 2009-04-09 | 2014-09-24 | 开利公司 | Refrigerant vapor compression system with hot gas bypass |
| CN105180513A (en) * | 2014-04-04 | 2015-12-23 | 江森自控科技公司 | Heat Pump System With Multiple Operating Modes |
| EP3144603A1 (en) * | 2015-09-16 | 2017-03-22 | Heatcraft Refrigeration Products LLC | Cooling system with low temperature load |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2684845B2 (en) * | 1990-11-30 | 1997-12-03 | ダイキン工業株式会社 | Operation control device for air conditioner |
| JP2005257237A (en) * | 2004-03-15 | 2005-09-22 | Sanyo Electric Co Ltd | Refrigeration unit |
| JP4859480B2 (en) | 2006-02-21 | 2012-01-25 | 三菱重工業株式会社 | Turbo chiller, control device thereof, and control method of turbo chiller |
| WO2008130357A1 (en) * | 2007-04-24 | 2008-10-30 | Carrier Corporation | Refrigerant vapor compression system and method of transcritical operation |
| US9810464B2 (en) * | 2012-04-27 | 2017-11-07 | Mitsubishi Electric Corporation | Air-conditioning apparatus with low outside air temperature mode |
| DE102013210175A1 (en) * | 2013-05-31 | 2014-12-18 | Siemens Aktiengesellschaft | Heat pump for use of environmentally friendly refrigerants |
-
2017
- 2017-03-31 DE DE102017205484.0A patent/DE102017205484A1/en not_active Ceased
-
2018
- 2018-03-28 CN CN201880022852.7A patent/CN110520683B/en active Active
- 2018-03-28 JP JP2019551521A patent/JP7074969B2/en active Active
- 2018-03-28 KR KR1020197031796A patent/KR102344187B1/en active IP Right Grant
- 2018-03-28 DK DK18716943.8T patent/DK3583365T3/en active
- 2018-03-28 EP EP18716943.8A patent/EP3583365B1/en active Active
- 2018-03-28 WO PCT/EP2018/057956 patent/WO2018178169A1/en unknown
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101512247A (en) * | 2006-09-11 | 2009-08-19 | 大金工业株式会社 | Refrigeration device |
| CN102388279B (en) * | 2009-04-09 | 2014-09-24 | 开利公司 | Refrigerant vapor compression system with hot gas bypass |
| CN105180513A (en) * | 2014-04-04 | 2015-12-23 | 江森自控科技公司 | Heat Pump System With Multiple Operating Modes |
| EP3144603A1 (en) * | 2015-09-16 | 2017-03-22 | Heatcraft Refrigeration Products LLC | Cooling system with low temperature load |
Also Published As
| Publication number | Publication date |
|---|---|
| EP3583365A1 (en) | 2019-12-25 |
| CN110520683B (en) | 2021-12-21 |
| JP7074969B2 (en) | 2022-05-25 |
| KR20190130158A (en) | 2019-11-21 |
| WO2018178169A1 (en) | 2018-10-04 |
| KR102344187B1 (en) | 2021-12-30 |
| DK3583365T3 (en) | 2022-08-29 |
| EP3583365B1 (en) | 2022-06-08 |
| JP2020512519A (en) | 2020-04-23 |
| DE102017205484A1 (en) | 2018-10-04 |
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