• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    ORC to convert heat from a heat source (11) containing compressed gas into mechanical energy, the ORC (8) comprising a closed circuit (14) containing a biphasic working fluid, the circuit (14) having a fluid pump (15) ) for circulation of the working fluid in the circuit (14) successively through an evaporator (10) in thermal contact with the heat source (11); by an expansion device (12) such as a turbine for converting the thermal energy of the working fluid into mechanical energy; and by a condenser (16) in thermal contact with a cooling element (17) characterized in that the ORC (8) is provided with means (21) for determining the mechanical energy generated by the expansion device (12) and a control device (22) that controls the vapor fraction of the working fluid that flows into the expansion device (12) based on the determined mechanical energy such that it is maximum.
    公开号:BE1023904B1
    申请号:E2016/5643
    申请日:2016-08-17
    公开日:2017-09-08
    发明作者:Henrik Öhman
    申请人:Atlas Copco Airpower Naamloze Vennootschap；
    IPC主号:
    专利说明:

    ORC for the inverter, waste heat from a heat source in mechanical energy and compressor installation that uses such an ORC.
    The present invention relates to an ORC for converting waste heat from a heat source into mechanical energy and a compressor installation that uses such an ORC to convert the waste heat from compression into mechanical energy.
    Energy cycles to convert waste heat into energy (WTP) are well described, such as ORC, Kalina, Trilatéral Flash etc.
    Such energy cycles are designed to recover waste heat that is produced, for example, by a compressor, and to convert that energy into useful mechanical energy that can be used, for example, to drive a generator for generating electrical energy.
    The use of an ORC (Organic Rankine Cycle) is known in particular to recover waste energy from heat sources with a relatively high temperature, such as the heat from compressed gas produced by a compressor installation.
    Such known ORCs include a closed circuit containing a two-phase operating fluid, the circuit further comprising a fluid pump for pumping the fluid around the circuit sequentially through an evaporator which is in thermal contact with the heat source to vaporize the working fluid; by an expansion device such as a turbine to convert the thermal energy sent to the gaseous working fluid produced in the evaporator into useful mechanical energy; and finally through a condenser in thermal contact with a coolant such as water or ambient air to transform the gaseous working fluid into a liquid that can be sent back to the evaporator for the next working fluid working cycle.
    In compressor installations, the ORC is used to cool the hot gases produced by compression, by bringing those hot gases into contact with the ORC evaporator and at the same time using the ORC to recover the heat recovered in the evaporator in useful energy in the expansion device.
    The waste heat in compressor installations is available at relatively high temperatures, usually 150 ° C or higher. At the same time, the cooling should lower the hot compressed gases to very low temperature levels, usually lower than 10 ° C above the temperature of the working fluid at the inlet of the evaporator.
    The known energy cycles for WTP, designed to work between the temperature levels of the working fluid such as cooling water and the compressed gas, represent a performance dilemma in the sense that they have to choose between two alternatives.
    Either the energy cycle uses all available waste heat that is available in the compressed gas, but then suffers from a very low cycle efficiency or the energy cycle uses only a part of the heat and the compressed gas will then only partially cool but with a relatively high efficiency. In the latter case, a separate air cooler is needed after the evaporator in the energy cycle to achieve proper cooling of the compressed gas.
    The known energy cycles are adapted to be suitable for heat sources such as compressed gas, which have the difficulty that the temperature of the compressed gas varies, which means that the available waste heat varies over time.
    A first approach is to cool the compressed gas with a coolant, often water, then cool the coolant with an energy cycle, which in turn is cooled by cooling water or ambient air. This solution causes very large thermodynamic losses due to the heat exchange over large temperature differences, and leads to a very low system efficiency.
    A second approach works with evaporation at varying temperatures, such as Kalina cycles and supercritical ORC. Also an ORC that works with zeotropic fluid mixtures as working flux is a well-known approach to reducing thermodynamic losses due to evaporation at varying temperatures. This approach leads to technically complex and therefore expensive systems.
    It is an object of the present invention to provide a solution to one or more of the aforementioned and other disadvantages.
    Therefore, it is an object of the invention to provide an ORC for converting heat from a heat source containing compressed gas into mechanical energy, the ORC comprising a closed circuit containing a two-phase operating flux, the circuit comprising a flux dump pump for the circulation of the working flux in the circuit successively through an evaporator which is in thermal contact with the heat source; by an expansion device such as a turbine for converting the thermal energy of the working flux to mechanical energy; and by a condenser in thermal contact with a cooling element, characterized in that the ORC is provided with means for determining the mechanical energy generated by the expansion device and a control device that controls the vapor fraction of the working flux flowing into the expansion into a device, wherein the control device controls the aforementioned vapor fraction on the basis of the determined mechanical energy such that the mechanical energy generated by the expansion device is maximum.
    By controlling the vapor fraction, the ratio of liquid / gaseous or vaporous working flux flowing into the expansion device will be adjusted.
    The mechanical energy generated by the expansion device can be considered as the power output from the ORC.
    An advantage of such an ORC according to the invention is that it uses a variable vapor fraction at the inlet of the expansion device adapted to the temperature variations of the compressed gas, such that a higher efficiency can be obtained compared to conventional ORC and Trilatéral Flash cycles.
    Another advantage is that an ORC according to the invention is less complex and less expensive than systems with variable evaporation temperature such as Kalina cycles, supercritical ORCs and ORCs with zeotropic fluid mixtures.
    It is important to note that in the evaporator, which is in thermal contact with the compressed gas, the working fluid will be heated to its boiling temperature and afterwards to at least partially evaporate the working fluid.
    In other words, the ratio of heat used for preheating to the heat used for evaporation increases by evaporating only part of the working fluid.
    This mixture of liquid working fluid and vaporized or vaporous or gaseous working fluid will flow into the expansion device.
    For example, by reducing the pumping capacity, the amount of liquid working fluid that is evaporated in the evaporator can be increased, i.e. more heat is used for the evaporation.
    That will reduce the average temperature difference in the evaporator between the working fluid that absorbs heat and the compressed gas that releases heat, while at the same time maintaining the physical vaporizing temperature of the fluid.
    That will be the performance dilemma i.v.m. dissolve the temperature difference between the working fluid and the compressed gas with which the known energy cycles for WTP are confronted, as explained above.
    According to a preferred embodiment, the control device controls the vapor fraction of the working fluid flowing into the expansion device by varying the working fluid flowing through the pump and / or by varying the working fluid flowing through the expansion device.
    The working fluid flowing through the pump or expansion device varies means that the power of the pump or expansion device is varied.
    The control device will control the power of the pump and / or expansion device and consequently control the vapor fraction of the working fluid that enters the expansion device as a function of the mechanical energy generated by the expansion device. More specifically, the control device will control the power of the pump and / or expansion device such that that mechanical energy is maximum.
    However, it is clear that many other control mechanisms are conceivable for varying the vapor fraction of the working fluid entering the expansion device. Any control that varies the vapor fraction of the working fluid that enters the expansion device can be used for the present invention.
    Preferably, the control device will continuously control the vapor fraction of the working fluid that flows into the expansion device.
    Such a control allows a variable vapor fraction of the working fluid that enters the expansion device.
    This means that the control device will respond to changing operating conditions such that optimum efficiency, i.e. a maximum energy output of the WTP cycle, can be achieved in all operating conditions.
    The present invention also relates to a compressor installation comprising a compressor element for compressing a gas and a cooler for cooling the compressed gas, wherein the compressor installation also comprises an ORC circuit according to the invention and wherein the aforementioned cooler is integrated in a heat exchanger in which also the ORC evaporator is integrated for heat transfer between the cooler and the evaporator.
    With the insight to better demonstrate the characteristics of the invention, a few preferred embodiments of an OCR according to the present invention for converting waste heat from a heat source into mechanical energy and from a compressor installation are described below as an example without any limiting character. uses such an OCR, with reference to the accompanying drawings, in which:
    Figure 1 schematically represents a single-stage compressor installation that uses an ORC system according to the invention;
    Figure 2 schematically represents a multi-stage compressor installation according to the invention;
    Figures 3 to 4 show different embodiments of the multi-stage compressor installation according to Figure 2.
    The compressor installation 1 shown in Figure 1 comprises a compressor element 2 with an inlet 3 and an outlet 4 and driven by a motor 5 for compressing a gas stream Q and a cooler 6 for cooling the compressed gas before it is supplied to a network 7 from consumers of compressed gas.
    The aforementioned gas can for example be air or nitrogen. But the invention is not limited to this.
    The compressor installation 1 further comprises an ORC 8 according to the invention in which the aforementioned cooler 6 is integrated in a heat exchanger 9 in which also the evaporator 10 of the ORC 8 is integrated for recovering the waste heat of the compressed gas used as a heat source 11 and for converting said heat into useful mechanical energy by means of an expansion device 12 of the ORC 8, for example a turbine which drives an electric generator 13 as illustrated in the example of Figure 1.
    The ORC 8 comprises a closed circuit 14 which contains a biphasic organic working fluid with a boiling temperature that is lower than the temperature of the heat source 11, i.e. the compressed gas, the working fluid being continuously pumped around in the circuit 14 by means of a fluid pump 15 in the direction indicated by the arrows F.
    The working fluid is such that it flows successively through the evaporator 10 which is in thermal contact with the heat source 11; then through the expansion device 12 and finally through a condenser 16 before being re-launched by the pump 15 for a subsequent cycle in the circuit 14.
    The condenser 16 is, in this example, in thermal contact with a cooling element 17 of a cooling circuit 18 which, in the example of Figure 1, is represented as a supply of cold water W taken from a tank 19 to circulate through the condenser 16 by means of a pump 20.
    According to the invention, the ORC 8 is provided with means 21 for determining the mechanical energy generated by the expansion device 12.
    Said means 21 can for instance be an energy meter or energy sensor.
    The ORC 8 is further provided with a control device 22 which can control the vapor fraction of the working fluid that enters the expansion device 12.
    The normal operation of the ORC 8 according to the invention is that the control device 22 will control the aforementioned vapor fraction on the basis of the mechanical energy determined by the means 21 such that the mechanical energy is maximum.
    In the example of Figure 1 and according to a preferred feature of the invention, the control device 22 will control the vapor fraction of the working fluid entering the expansion device 12, by varying the working fluid flowing through the pump 15 and by the working fluid flowing through the expansion device 12 flows.
    It is of course also possible that the control device 22 controls only the expansion device 12 or only the pump 15.
    In that case, however, the control device 22 will control the vapor fraction of the working fluid entering the expansion device 12 by repeatedly switching between two control algorithms.
    A first control algorithm consists in varying the working fluid flowing through the pump 15 until the mechanical energy generated by the expansion device 12 locally reaches a maximum.
    The second control algorithm consists in varying the working fluid flowing through the expansion device 12 until the mechanical energy generated by the expansion device 12 reaches a further optimized maximum.
    The control device 22 will vary the working fluid flowing through the expansion device 12 or the pump 15, i.e. the power of the expansion device 12 or pump 15 varies, and at the same time determine the mechanical energy generated by the expansion device 12, i.e. determine the power output of the ORC, and will select the power of the expansion device 12 or pump 15 for which the determined power output of the ORC is maximum.
    After the first control algorithm, the ORC power delivery will be optimized as a function of only the power of the pump 15. That means that the ORC power delivery will be maximally too local.
    By applying the second control algorithm, the ORC power delivery will be optimized as a function of the power of the expansion device 12, such that an optimized maximum can be achieved.
    By switching again to the first control algorithm, the ORC power delivery will be optimized again in function of the pump 15, such that changes in operating conditions can and will be taken into account.
    Such changes in operating conditions are: changes in the temperature of the compressed air to be cooled, changes in the compressed air flow, changes in the ambient temperature, changes in the cooling water flow, changes in the cooling water temperature or changes in the efficiency of the heat exchanger.
    By applying such a control, the control device 22 will continuously control the vapor fraction of the working fluid that enters the expansion device 12, such that changes in operating conditions can easily be anticipated.
    In this way, a maximum ORC power delivery can be guaranteed in all operating conditions.
    Various options are possible to vary the working fluid flow through the expansion device 12.
    The power of the expansion device 12 can be varied by varying the speed of the expansion device 12, as in the present example or by means of a bypass over the expansion device 12, by means of sliding valves and / or lifting valves, by varying the stroke volume of the expansion device 12 or by varying the oil injection of the expansion device 12.
    Various options are also possible to vary the working fluid flow through the pump 15.
    The power of the pump 15 can be varied by varying the speed of the pump 15, as in the present example or by means of a bypass over the pump 15, by varying the stroke volume of the pump 15 or by varying the on / off to vary the frequency of the pump 15.
    According to a preferred embodiment of the invention, the vapor fraction of the working fluid entering the expansion device 12 is between 10% and 99% mass fraction. It is of course also possible that the vapor fraction of the working fluid entering the expansion device 12 is kept between other limits, for example between 20% and 95% mass fraction or between 40% and 90% mass fraction.
    The expansion device 12 can be any type of expansion device 12 that can generate mechanical energy through expansion of a biphasic fluid, i.e. a mixture of liquid and gaseous working fluid. Preferably, a volumetric expansion device 12 such as a screw expansion device 12 or a mechanical cylinder or the like that can take on a mixture of liquid and gaseous working fluid.
    The compressor element 2 can also be of any type, in particular an oil-free air compressor element 2.
    It is also clear that the cooling of the condenser 16 can be realized in other ways than in the example of Figure 1, for example by blowing ambient air over the condenser 16 with the aid of a fan or the like.
    Preferably a working fluid is used whose boiling temperature is lower than 90 ° C or even lower than 60 ° C, depending on the temperature of the available heat source 11, i.e. the temperature of the compressed gas to be cooled.
    An example of a suitable organic working fluid is 1,1,1,3,3-pentafluoropropane. The working fluid could be mixed with a suitable lubricant for the lubrication of at least a portion of the moving parts of the ORC 8. The working fluid itself could also act as a lubricant, meaning that a working fluid having lubricating properties is selected.
    Figure 2 shows a multi-stage compressor installation 1 according to the invention with in this case two compressor elements, a first-stage compressor element 2 'and a last-stage compressor element 2 ", respectively, the elements 2' and 2" being driven via a gearbox 23 by a single motor 5 and in series are connected to compress a gas into two incremental pressure stages.
    The compressor elements 2 ", 2" can also be of any type, in particular oil-free air compressor elements.
    The installation 1 is provided with an intermediate cooler 6 'for cooling the gas which is compressed by the first-stage compressor element 2' before it is fed to the next element 2 "and an aftercooler 6" for cooling the gas which is compressed by the last stage compressor element 2 "before it is sent to the network 7.
    Each of the aforementioned coolers 6 'and 6 "is integrated into a heat exchanger 9' and 9", in which also a part of the evaporator 10 of the ORC 8 is integrated.
    In the example shown, the ORC comprises two evaporators! devices 10 'and 10 "connected in series in the circuit 14, although it is not excluded that the ORC comprises only one evaporator 10 of which a part 10' is in thermal contact with the intercooler 6 ', while another part 10" is in thermal contact with the aftercooler 6 ".
    Also in this case the control device 22 will be controlled according to the same method as in Figure 1.
    In that case, the same advantages apply as with the single-stage compressor element of Figure 1.
    Figure 3 shows another example of a multi-stage compressor installation 1 according to the invention that differs from the embodiment of Figure 4 in that the evaporators 10 'and 10 "are connected in parallel instead of in series, but still with the same advantages.
    Figure 4 illustrates an alternative to the installation 1 of Figure 3 wherein the installation additionally includes a three-way valve 24 to split the working fluid flow coming from the pump 15 into two suitable separate flows through the evaporation devices 10 'and 10 ".
    Instead of using a three-way valve 24, one or two restrictions or a combination of a restriction and a valve could be used in the taps of the parallel circuit connecting the evaporators 10 'and 10 ".
    The present invention is by no means limited to the embodiments described by way of example and shown in the figures, but such an ORC according to the invention for converting waste heat from a heat source into mechanical energy and a compressor installation using such an ORC can be realized in all kinds of variants without departing from the scope of the invention.
    权利要求:
    Claims (17)
    [1]
    1.- ORC (Organic Rankine Cycle) to convert heat from a heat source (11) containing compressed gas into mechanical energy, the ORC (8) comprising a closed circuit (14) containing a two-phase operating fluid, the circuit (14) comprising a fluid pump (15) for circulating the working fluid in the circuit (14) sequentially through an evaporator (10) in thermal contact with the heat source (11); by an expansion device (12) such as a turbine for converting the thermal energy of the working fluid into mechanical energy; and characterized by a condenser (16) in thermal contact with a cooling element (17); that the ORC (8) is provided with means (21) for determining the mechanical energy generated by the expansion device (12) and a control device (22) that controls the vapor fraction of the working fluid that is in the expansion device ( 12) flows in, wherein the control device (22) controls the aforementioned vapor fraction on the basis of the determined mechanical energy such that the mechanical energy generated by the expansion device (12) is maximum.
    [2]
    ORC according to claim 1, characterized in that the control device (22) controls the vapor fraction of the working fluid flowing into the expansion device (12) by varying the working fluid flowing through the pump (15) and / or by vary the working fluid flowing through the expansion device (12).
    [3]
    OCR according to claim 1 or 2, characterized in that the control device (22) continuously controls the vapor fraction of the working fluid that flows into the expansion device (12).
    [4]
    The ORC according to claim 2 or 3, characterized in that the control device (22) controls the vapor fraction of the working fluid flowing into the expansion device (12) by repeatedly switching between two control algorithms, the first control algorithm consisting of the varying the working fluid flowing through the pump (15) until the mechanical energy generated by the expansion device (12) locally reaches its maximum and the second control algorithm consists of varying the working fluid flowing through the expansion device (12) until the mechanical energy generated by the expansion device (12) reaches a further optimized maximum.
    [5]
    ORC according to one of the preceding claims 2 to 4, characterized in that the variation of the working fluid flowing through the expansion device (12) is realized by means of a bypass over the expansion device (12), by by varying the speed of the expansion device (12), by means of sliding valves and / or lifting valves, by varying the stroke volume of the expansion device (12) or by varying the oil injection of the expansion device (12).
    [6]
    OCR according to one of the preceding claims 2 to 5, characterized in that the variation of the working fluid flowing through the pump (15) is realized by means of a bypass over the pump {15), due to the speed of the pump (15), by varying the stroke volume of the pump (15) or by varying the on-off frequency of the pump (15).
    [7]
    ORC according to one of the preceding claims, characterized in that the vapor fraction of the working fluid entering the expansion device (12) is between 10% and 99% of the mass fraction.
    [8]
    The ORC according to one of the preceding claims, characterized in that the expansion device (12) is of any type suitable for accepting a mixture of liquid and gaseous working fluid.
    [9]
    The ORC according to any of the preceding claims, characterized in that the expansion device (12) is a volumetric expansion device (12) or that the expansion device (12) is a screw expansion device (12).
    [10]
    The ORC according to any of the preceding claims, characterized in that a working fluid is used which comprises a lubricant or which acts as a lubricant.
    [11]
    ORC according to one of the preceding claims, characterized in that a working fluid is used whose boiling temperature is lower than 90 ° C, preferably lower than 60 ° C.
    [12]
    Compressor installation comprising a compressor element (2) for compressing a gas and a cooler (6) for cooling the compressed gas, characterized in that the compressor installation (1) comprises an ORC (8) according to one of the preceding claims, wherein said cooler (6) is integrated in a heat exchanger (9) in which also the evaporator (10) of the ORC (8) is integrated for heat transfer between the cooler (6) and the evaporator (10).
    [13]
    Compressor installation according to claim 12, characterized in that it is a multi-stage compressor installation (1) with at least two compressor elements (2 ', 2 ") connected in series to compress a gas and at least two coolers (6', 6") that either act as an intermediate cooler (6 ') between two compressor elements (2', 2 ") or as an aftercooler (6") to cool the gas compressed by the compressor element (2 ") in the final stage, the compressor installation ( 1) comprises an ORC (8) with at least one evaporator (10), each of the aforementioned cooler (6 ', 6 ") being integrated in a heat exchanger (9', 9") in which also at least a part of the evaporator (10) of the ORC (8) is integrated.
    [14]
    Compressor installation according to claim 13, wherein the evaporator (10) of the ORC (8) is composed of a plurality of evaporator devices or parts of an evaporator device (10 ', 10 "), each evaporator device or part of the evaporator device being integrated with a intercooler (2 ') or with an aftercooler (2 ") in a heat exchanger (9', 9"), the evaporators or parts of the evaporator (10 ', 10 ") of the ORC (8) being in series or connected in parallel in the ORC circuit (14) that a fluid flow is possible.
    [15]
    Compressor installation according to claim 14, characterized in that the evaporation devices or the parts of the evaporation device (10 ', 10 ") are connected in parallel and that means are provided for splitting the flow of working fluid coming from the pump (15) in separate streams through the evaporators or parts of the evaporators (10 ', 10 ").
    [16]
    Compressor installation according to claim 15, characterized in that the means for distributing the flow of working flux to the evaporation devices or parts of the evaporation device (10 ', 10 ") is formed by a three-way valve (24) or by a restriction and / or a valve.
    [17]
    Compressor installation according to one of claims 12 to 16, characterized in that the compressor element (2) or: the compressor elements (2 ', 2 ") are oil-free air compressor elements.
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    法律状态:
    2017-12-13| FG| Patent granted|Effective date: 20170908 |
    优先权:
    申请号 | 申请日 | 专利标题
    US201562215247P| true| 2015-09-08|2015-09-08|
    US62215247|2015-09-08|CN201680059956.6A| CN108474271B|2015-09-08|2016-08-18|ORGANIC Rankine cycle for converting waste heat from a heat source into mechanical energy and compressor device utilizing same|
    US15/757,299| US10788203B2|2015-09-08|2016-08-18|ORC for transforming waste heat from a heat source into mechanical energy and compressor installation making use of such an ORC|
    HUE16790511A| HUE046685T2|2015-09-08|2016-08-18|Orc for transforming waste heat from a heat source into mechanical energy and compressor installation making use of such an orc|
    CA2997573A| CA2997573C|2015-09-08|2016-08-18|Orc for transforming waste heat from a heat source into mechanical energy and compressor installation making use of such an orc|
    PL16790511T| PL3347574T3|2015-09-08|2016-08-18|Orc for transforming waste heat from a heat source into mechanical energy and compressor installation making use of such an orc|
    RSP20191075| RS59342B1|2015-09-08|2016-08-18|Orc for transforming waste heat from a heat source into mechanical energy and compressor installation making use of such an orc|
    EP16790511.6A| EP3347574B1|2015-09-08|2016-08-18|Orc for transforming waste heat from a heat source into mechanical energy and compressor installation making use of such an orc|
    BR112018004559A| BR112018004559A2|2015-09-08|2016-08-18|orc to transform waste heat from a heat source into mechanical energy and compressor installation by making use of such orc|
    RU2018112448A| RU2698566C1|2015-09-08|2016-08-18|Organic rankine cycle for conversion of waste heat of heat source into mechanical energy and compressor plant using such cycle|
    PCT/BE2016/000038| WO2017041146A1|2015-09-08|2016-08-18|Orc for transforming waste heat from a heat source into mechanical energy and compressor installation making use of such an orc|
    JP2018530943A| JP6679728B2|2015-09-08|2016-08-18|Organic Rankine cycle for converting waste heat from a heat source into mechanical energy and compressor equipment utilizing such organic Rankine cycle|
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