• 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:
    Apparatus (20) and method for converting low temperature thermal energy into higher temperature thermal energy by mechanical energy and vice versa with a closed loop recycle fluid rotor (21), said rotor (21) comprising a compressor unit (23) having a plurality of compression channels (25) and a relaxation unit (24) having a plurality of expansion channels (26), wherein the rotor (21) further comprises heat exchangers (1 ', 1' ') for heat exchange between the working medium and a heat exchange medium, and with a relative to the Rotor (21) rotatable paddle wheel (30), wherein the paddle wheel (30) between in the heat pump operating state, the flow of the working medium supplying supply channels (31) and at least one in the heat pump operating state, the flow of the working fluid dissipating discharge channel (32) of the rotor (21) is arranged, wherein the supply channels (31) are substantially parallel to R have individual axes of the working medium from the supply channels (31) substantially parallel to the axis of rotation (22) in the impeller (30) are feasible.
    公开号:AT515217A4
    申请号:T50296/2014
    申请日:2014-04-23
    公开日:2015-07-15
    发明作者:
    申请人:Ecop Technologies Gmbh；
    IPC主号:
    专利说明:

    The invention relates to a device for converting thermal energy of low temperature into thermal energy of higher temperature by means of mechanical energy and vice versa with a rotor rotatably mounted about a rotation axis for a closed cycle continuous working medium, the rotor a compressor unit with a plurality of compression channels, in which flows of the working medium for increasing the pressure with respect to the axis of rotation can be guided substantially radially outward, and a relaxation unit with a plurality of expansion channels, in which flows of the working medium for pressure reduction with respect to the axis of rotation can be guided substantially radially inwards, the rotor further comprising heat exchangers for heat exchange between the working fluid and a heat exchange medium, and a paddle wheel rotatable relative to the rotor for maintaining in a heat pump operating condition the flow of the working medium is provided around the axis of rotation of the rotor and / or in a condition of the operating state for utilizing the flow energy of the working medium.
    Furthermore, the invention relates to a method for converting thermal energy of low temperature into thermal energy of higher temperature by means of mechanical energy and vice versa, whereby a working medium in a rotor rotating about a rotation axis passes through a closed cycle, wherein a plurality of flows of the working medium for increasing the pressure in With reference to the axis of rotation are guided substantially radially outward, where the flows of the working medium for pressure reduction with respect to the axis of rotation are guided substantially radially inwardly, wherein a heat exchange between the Arbeitsmedi¬um and a heat exchange medium is made, wherein the working medium in a heat pump operating condition for maintaining the flows of the working medium about the axis of rotation of the rotor and / or in a generator operating condition for utilizing the flow energy of the working medium through a paddle wheel.
    From the prior art are already rotating Wärmepumpenbzw. Heat engines known in which a gaseous Arbeits¬ medium is performed in a closed thermodynamic cycle process.
    In WO 2009/015402 Al a heat pump is described, both the working medium in a piping system of a rotor a cyclic process with the steps a) compression of the working medium, b) heat removal from the working medium by means of a heat exchanger, c) relaxation of the working medium and d) heat supply to the working medium passes through another heat exchanger. The increase in pressure or pressure reduction of the working medium is predominantly due to the centrifugal acceleration, the working medium flowing radially outwards in a compression unit with respect to a rotation axis and radially inward in a tensioning unit. The removal of heat from the working medium to a heat exchange medium of the heat exchanger takes place in an axial or parallel to the axis of rotation running portion of the pipeline system, which is associated with a co-rotating, the heat exchange medium exhibiting heat exchanger.
    Moreover, in this prior art, a paddle wheel has been used which is particularly used to maintain the flow of the working fluid in a rotary operation. On the one hand, the impeller can be arranged in a rotationally fixed manner, with a relative movement to the pipeline system leading to the working medium resulting from the rotationally fixed arrangement. On the other hand, it has already been proposed that the impeller is associated with a motor for generating a relative movement to the piping system. Further, in this device, the display wheel may be connected to a generator to convert the generated shaft power into electrical energy by the relative movement of the paddle wheel.
    In the prior art a wide variety of paddle wheels for maintaining a fluid flow are known, such Schau¬felräder can be designed as a compressor, expansion turbines or Leiträder. In the prior art are known as Grenzfor¬men for the flow of paddle wheels on the one hand axi¬ale and on the other radial embodiments. In Mischfor¬men such as diagonally flowed paddle wheels largely the same considerations apply to the radial or axial Strömungsungskom¬ component. When using axially flown paddle wheels, so-called axial fans (or generally axial compressor) or axial turbines, a conventional Di¬mensionierung can be applied substantially. However, the axial design has the disadvantage that lower pressure increases can be effected in comparison to the radial design, whereby the axial impeller wheels usually have to be constructed in multiple stages. In a multi-stage design, idler vanes are mounted between the vaned wheels to redirect the flow. This creates a swirl with the rotation of the surrounding rotating axial vanes, substantially completely eliminating the swirl from the flow, or twisting against the turntable Generated. With regard to the installation of radial Schaufelrä¬ which have the advantage over axial blade wheels of higher pressures per stage and therefore can often be carried out in one stage, has been used on a variant, as it is also used in multi-stage centrifugal or Zentripe-dalturbinen, in which the paddle wheels are arranged in a stationary housing.
    Extensive tests have shown, however, that the prior art arrangement of the paddle wheels of the apparatus according to the invention, in which the supply and discharge of the paddle wheel are arranged in a rotating manner in the rotor housing, does not provide satisfactory results. It has been observed that, for example, the efficiency of a radial ventilator drops from 80% with a non-rotating housing to 25% with a rotating housing.
    Accordingly, there is a great need for improvements on the paddlewheels in order to better account for the complex constraints during the multiple-step process within the rotor.
    The object of the present invention is therefore to provide a doping device for converting thermal energy, as stated at the beginning, in which the disadvantages of the prior art are eliminated or at least significantly alleviated. Accordingly, the invention is in particular the goal of maintaining the flow of the working medium about the axis of rotation with the lowest possible energy losses.
    According to the invention, the impeller is disposed between discharge conduits feeding the flow of the working medium in the heat pump operating state and at least one discharge channel of the rotor discharging in the heat pump operating state, wherein the supply channels extend substantially parallel to the axis of rotation and extend directly in front of an inlet opening of the impeller, so that individual flows of the working medium from the supply ducts can be guided into the blade wheel substantially parallel to the axis of rotation.
    Accordingly, the invention is based on the surprising finding that the efficiency of the paddle wheel can be significantly improved by the fact that the working medium before entering the paddle wheel in individual flows parallel to the axis of rotation, i. in the axial direction, is guided. For the purposes of this disclosure, the extension of the outlet sections of the supply ducts to just in front of the impeller means that the flows of the working medium in the supply ducts are not brought together, but are fed to the impeller separately from one another. The outlet sections of the inlet channels are preferably arranged at regular angular intervals and at the same radial distance around the axis of rotation. Thus, several axial flows of the working fluid are introduced into the bucket wheel. Thereafter, the working fluid flows into the at least one discharge channel of the rotor. Thus, the working medium from the paddle wheel becomes direct, i. without the interposition of a standstill housing, led into the rotor. The rotor therefore forms a rotating housing for the paddle wheel, which preferably completely surrounds the paddle wheel. The working medium is thus guided through the impeller wheel located inside the rotor, wherein the working medium is not guided in a stationary housing, unlike the prior art. As a result, the flow energy of the working medium can essentially be maintained during the passage through the cyclic process. It is also advantageous that dynamic seals of the working medium to the environment are not required. In the conventional design of paddle wheels was a stationary
    Housing provided. On the other hand, in the device according to the invention, a rotor is provided so that the components surrounding the impeller rotate during operation. In order to take into account the different installation situation, it would have been obvious to consider only the relative speeds between the impeller and the rotor, i. the differential speed zwi¬schen the absolute rotor speed and the absolute Schaufelrad¬ speed. However, it has been shown that this consideration fundamentally fails. In the radial flow of the working medium, which is customary in the prior art, from the rotating supply ducts into the blade wheel, a swirl occurs at the radial exit from the supply duct, in particular by the acceleration of the Coriolis System seen from radially inwardly entge¬gen the direction of rotation is formed. This twist significantly changes the characteristic of the inflow, in particular the speed triangles, whereby a dimensioning according to conventional methods had to be unsuccessful. According to the invention, however, the working medium is led out in the axial direction from the supply channels conveying the working medium. This advantageously results in the Coriolis acceleration approaching zero and zero or no substantial twist. As a result, the passage into the paddle wheel is easier to calculate and advantageously also not dependent on the rotational speeds of the paddle wheel and the surrounding housing of the rotor, nor on the relative flow speed.
    In order to enable stable operation, it is advantageous if the smallest possible number of radial Ableitungskanä¬len is connected to the impeller. The lower the number of connected radial discharge channels, the more stable is the operation, since the probability of a flow separation of a discharge channel with decreasing number of discharge channels is always lower. In a preferred embodiment, therefore, exactly one discharge channel per impeller is provided. In this embodiment, therefore, exactly one paddle wheel is provided for each discharge channel which is guided radially outward, wherein a plurality of paddle wheels (and a corresponding number of discharge channels) may be provided. For reasons of cost-effectiveness, it is provided in an alternative preferred embodiment that the impeller is connected to at least three discharge channels. Preferably, no more than twelve discharge channels are connected to the paddle wheel. However, it is quite possible for a radial discharge channel in the region remote from the axis, preferably after a deflection in the axial direction, to be divided into a plurality of heat exchanger passages.
    In order to achieve pressure differences with high efficiencies when flowing through the compression and expansion channels, but to reliably prevent the formation of swirl flows prior to entry into the impeller, it is favorable if the supply channels have feed lines which extend substantially in the radial direction and which extend between the outlet sections and are arranged with respect to the axis of rotation of internal heat exchangers. The supply line sections are preferably longer than the exit sections of the supply line.
    In order to effect a heat exchange between the working medium and a heat exchange medium at a higher temperature, it is favorable if the at least one discharge channel is connected to the compression channels which are connected to outer heat exchangers with respect to the axis of rotation.
    In order to maintain the cycle in operation with the lowest possible Energie¬aufwand, it is advantageous if the paddle wheel is arranged in the radial direction closer to the axis of rotation than the inner heat exchanger, wherein the paddle wheel is preferably arranged konzententric about the axis of rotation of the rotor. Accordingly, the axes of rotation of the rotor and the impeller are preferably aligned. As a result, a particularly efficient driving mode can be achieved.
    In order to convert the radial flows of the working medium in the supply ducts into axial flows prior to entry into the impeller, it is advantageous if the supply ducts have arcuately curved walls at the outlet sections, which divert the working medium by substantially 90 ° from the Feed line sections in the outlet sections act. Through the arcuate walls of the expansion channel at the outlet end, the working medium can be continuously deflected into an axial flow, wherein the flows of the working medium are not or only slightly disturbed by the deflection.
    To isolate the flows of the working medium individually, i. essentially unmixed or separated from one another, into the blade wheel, it is advantageous if the outlet sections of the supply channels are formed between separating elements extending substantially in the radial and axial direction to the axis of rotation, in particular substantially planar partitions. By means of the arrangement of partition walls can be achieved in a particularly simple way that the axial flows of Arbeits¬mediums in the outlet sections of the supply channels unmixed and substantially free of twist with respect to the rotating rotor, which is the housing for the paddle wheel, are guided in the paddlewheel. For a better controllability, in particular in the partial load range, it is advantageous if the separating elements are adjustable in front of the paddle wheel. Advantageously, a defined entrance swirl can thus be generated, which can be adjusted via the separating elements. In contrast to the swirl occurring due to the Coriolis acceleration occurring in the state of the art at the entry into the impeller, this defined entrance swirl can be calculated or simulated in the design of the device. The device according to the invention is usually designed for a specific operating point. In particular, the inlet angle of the separating elements can be dimensioned in such a way that the flow, when viewed in the relative rotating impeller system, forms a continuous transition, ie. an inflow without significant change in direction, in the Schaufel¬ region of the impeller. At a change in the speed of the impeller and / or at varying relative flow velocities, that is to say when operating outside of the design point, the inflow angles of the flow usually change, as a result of which a discontinuous inflow would occur in the impeller region of the impeller. This effect reduces the efficiency of the impeller when operating outside the design point. In order to overcome this drawback, the separators for off-design operation may be adjusted such that the working fluid relative to the relative rotating impeller system flows in a steady manner upon entry into the blade area of the impeller. Thus, the efficiency can be increased. The paddle wheel can also generate a higher pressure and a higher maximum volume flow by this measure, whereby the Einsatzbe¬reich is extended.
    In order to maintain the flow of the working medium when passing through the cyclic process, it is favorable for the display wheel to have a plurality of, in particular arcuately curved, blades. The vanes accelerate the working fluid in the circumferential direction with respect to the axis of rotation before the working fluid is directed into the compression passages via exit ports between the outer edges of the blades of the impeller.
    According to a preferred embodiment, the impeller on the side facing the axis of rotation on a Rad¬alabschnitt free of blades on. In the annular radial section of the Schau¬felrads the guided separately in the feed channels flows of the working medium are merged. As a result, the working medium in the radial section can be homogenized before the working medium flowing radially outward from the radial section is accelerated by the rotating blades and then discharged into the discharge channels.
    In order to supply the working medium flowing in the axial direction to the blades, it is favorable if the blade wheel has an arcuately curved deflecting wall on the radial portion, with which the working medium can be deflected by substantially 90 ° in the radial direction.
    In order to substantially maintain the flow energy of the working medium, it is advantageous if the at least one discharge duct has an inlet section arranged obliquely to the radial direction, which is connected to a discharge section extending essentially in the radial direction. The inlet portion of the drainage channel preferably extends in the direction in which a steady transition of the flow, i. in which an inflow is present without significant Richt¬tungsänderung results. This is achieved in the design by vector addition. Accordingly, the working medium is introduced in the tangential direction, relative to a cross section in the generally circular envelope or outer surface of the Schau¬felrads, in the inlet sections, which are connected to the substantially extending in the radial direction Ableitungsab¬schnitten. The inlet sections and the sealing sections are preferably connected to one another via arcuately curved transition sections.
    In order to drive the paddle wheel and thus to accelerate the working medium during passage or to use the rotational energy of the paddle wheel, it is advantageous if the paddle wheel in particular has a rotatable Schaufelradwelle parallel to the axis of rotation of the rotor, which is connected to a motor or to a generator. Thus, on the one hand, the paddle wheel may be connected to a motor to produce relative movement between the rotor and the paddle wheel. In this embodiment, the impeller is set up in a heat pump operation state for maintaining the circulation of the working medium. On the other hand, the impeller may be connected to a generator to convert the shaft power present at the impeller shaft into electrical energy by the relative movement of the impeller. With such a use of the device, due to the different temperature levels at the heat exchangers, a flow in the nature of a natural circulation is obtained. The energy of the flow is then converted into shaft power in the turbine blade impeller which, in turn, is converted into electrical power by means of a generator. Preferably, part of this energy is spent on a motor that drives the rotor. In the present disclosure, the terms " entry " and "exit " on the function of the paddle wheel to maintain the flow of the working medium about the axis of rotation, i. When the paddle wheel is used in a heat pump operating condition as Ventila¬ gate. In the function of the paddle wheel as a turbine for generating electrical energy, the flow direction of the working medium is reversed so that, for example, the exit sections of the supply lines become the entry sections of the discharge lines.
    In a preferred embodiment, the axes of rotation of the Schau¬felrads and the rotor coincide. If the Schaufelradwelle aligned on the shaft of the rotor, asymmetric forces can vor¬teilhafterweise due Zentri¬fugalbeschleunigung on the storage of the paddle wheel arise. Preferably a separate motor / generator for the Schaufelrad- wave is provided so that the paddle wheel regardless of the rotor having the compression and expansion channels is drivable; in this case, the rotor is connected to a second motor. Alternatively, the same motor for driving the paddle wheel and the rotor or the same generator can be used for the utilization of the rotational energy of the paddle wheel and the rotor.
    It has surprisingly proven to be advantageous if the motor for rotating the impeller in the same direction of rotation as the rotor is equipped with the expansion and compression channels for the working medium. Advantageously, when the impeller is rotated in the same direction, the main rotor can again utilize the acceleration field of the main rotor. As a result, the efficiency of the impeller can be increased even more over an arrangement with non-rotating housing, since the compression ratio in the impeller itself is increased due to the centrifugal acceleration and this compression has a significantly higher efficiency than the pressure increase due to speed changes, for example, when passing from the impeller to the derivation channel follower.
    The device according to the invention utilizes the centrifugal acceleration as it flows through the compression and expansion channels of the rotor to produce different pressure or temperature levels of the working medium. For the conversion of thermal energy of the working medium by means of kinetic energy and vice versa, it is favorable if at least one external heat exchanger with respect to the rotational axis of the heat exchanger and at least one outer heat exchanger between the working medium and a heat exchange medium is provided. The heat exchangers are arranged co-rotating in the rotor. Depending on the direction of flow of the working medium, the device can be operated on the one hand as a heat pump, in which the rotor is rotated by a drive and the circulating flow is generated by a fan. The reverse flow direction corresponds to operation as a heat-power machine for generating electrical power, wherein different temperature levels are used to generate a flow, which is converted into mechanical energy in the turbine impeller, which is then converted into electrical energy in a generator. In this operating condition, the rotor is driven by a motor which is e.g. powered by the recovered electrical energy from the turbine.
    Preferably, the heat exchangers are arranged substantially parallel to the rotational axis of the rotor. The heat exchangers are herebetween the compression and expansion channels connected.
    The inner heat exchanger is provided for a heat exchange at niediger temperature and the outer heat exchanger for a heat exchange at a higher temperature.
    In order to increase the performance of the device, it is preferable that each of a plurality of internal heat exchangers and external heat exchangers is provided. Preferably, the inner heat exchangers on the one hand and the outer heat exchangers on the other hand are arranged at regular angular intervals with respect to the axis of rotation. Preferably, as many inner and outer heat exchangers as compaction and expansion channels are provided. Accordingly, the inner and outer heat exchangers are connected in pairs via a respective compression and expansion channel. Moreover, it is preferably provided that the number of supply and discharge channels for the impeller corresponds to the number of inner and outer heat exchangers.
    According to a further preferred embodiment, the number of internal heat exchangers corresponds to a multiple of the external heat exchanger or vice versa.
    The heat exchange can be made particularly efficient when the at least one inner heat exchanger and the at least one outer heat exchanger are substantially parallel to the axis of rotation, with the compression and expansion passages between the inner heat exchanger and the outer heat exchanger. Preferably, a plurality of inner heat exchangers and a plurality of outer heat exchangers are provided, which are each arranged at equal radial distances from the axis of rotation. In this embodiment, it is also preferable to provide a number of compression channels corresponding to the number of the inner and outer heat exchangers, respectively.
    Particularly preferred is an embodiment in which the Schau¬felrad several consecutively from the working medium through-flowable Schaufelradstufen. In this embodiment, the supply ducts have outlet sections extending substantially parallel to the axis of rotation and extending to just in front of the inlet opening of the first display wheel stage seen in the direction of flow. The successive Schaufel¬radstufen are each verbun¬ via a deflection with each other, with which the working fluid is deflected between the Schaufelradstu¬fen. Preferably, the deflection essentially comprises parallel to the axis of rotation extending outlet sections, which extend to immediately before the inlet opening of the following Schauforadstufe seen in the direction of flow direction. Thus, the working medium is always guided to the next Schau¬felradstufe and in the direction of the axis of rotation The last impeller stage seen in the flow direction is connected to the at least one discharge channel.
    In the cyclic process, a non-continuously increasing pressure difference on the impeller is observed for an increasing mass flow. Accordingly, especially at low mass flows and high rotational speeds of the rotor with increasing mass flow a fal¬lende pressure difference caused on the paddle wheel, before this again increases. For that reason it is favorable if one
    Paddle wheel is used, which has the steepest possible course, i. that at a certain speed of the impeller as well as a main rotor speed from reaching the maximum pressure a steeply sloping course is preferred. Such a course is achieved in particular with multi-stage paddle wheels. Since the process characteristic (ie the required pressure above the mass flow) and the blade characteristic (ie the pressure generated over the mass flow) usually have two cut points, but only one of them is a stable drive point, a vertical characteristic would be for the printers Production ideal. This could be realized, for example, by positive displacement machines (such as reciprocating engines). However, a mehr¬stufige pressure increase with paddle wheels achieved in vor¬teilhafter way a similar effect by from a bestimm¬ten point a very steep course is achieved.
    The object on which the invention is based is also achieved by a method of the type mentioned at the beginning, in which individual flows of the working medium in the heat pump operating state are conducted directly in front of the impeller and introduced into the impeller in a manner generally parallel to the axis of rotation. Accordingly, the currents of the working medium einzelbzw. separated from each other and guided in the axial direction in the Schau¬felrad.
    The advantages and technical effects of this process are evident from the above explanations, to which reference can be made herewith. Surprisingly, it has proved to be advantageous if the impeller is rotated in the same direction of rotation and at a higher absolute speed as the rotor with the expansion and Ver¬dichtungskanälen. As a result of the rotation of the blade wheel in the direction of rotation of the rotor, a higher absolute rotational speed of the blade wheel is provided, which causes a correspondingly higher centrifugal acceleration and thus a more efficient sealing of the working medium. With the same direction of rotation of the impeller and the rotor, the centrifugal compression effect is increased proportionally, thereby increasing the efficiency.
    The invention will be explained below with reference to preferred embodiments shown in the drawing, to which, however, it should not be restricted. In detail, in the drawing:
    1 shows schematically a perspective view of a device according to the invention for converting thermal energy, in which a working medium in a rotor passes through a closed cycle process, the cycle being closed by means of a rotating blade wheel;
    2 shows a longitudinal section through the device of FIG. 1, where only the components relevant to the function of the blade wheel are shown for the sake of clarity;
    FIG. 2a shows a temperature / entropy diagram of the cyclic process carried out in the device according to the invention; FIG.
    3 shows a longitudinal section of the device according to FIG. 1, 2 in the region of the paddle wheel;
    4 shows a cross-section of the device according to the line IV-IV in FIG. 2 in the area of the blade wheel, wherein the outlet sections of the supply channels on the one hand and the inlet sections of the discharge channels on the other hand can be seen;
    5 shows a schematic perspective view of parts of the rotor in the region of the supply ducts, which have outlet sections extending in the axial direction before entering the impeller;
    Fig. 6 schematically shows a perspective view of the bucket wheel of the device shown in Figs. 1 to 5; and
    7 shows a longitudinal section of the device according to FIG. 3 in the area of the blade wheel, which in the case of this embodiment has several blade wheel stages which can be flowed through one behind the other.
    1 shows a device 20 for the conversion of thermal energy of mechanical energy and vice versa, which is used in the ge shown embodiment as a heat pump. The device 20 comprises a rotor 21, which can be rotated about an axis of rotation 22 by means of a motor (not shown). The rotor 21 has a compressor unit 23 and a relaxation unit 24, which have flow channels for a working medium. When flowing through the rotor 21, the working medium, for example a noble gas, passes through a closed cycle process which comprises the steps a) compression of the working medium, b) heat exchange between the working medium and a heat exchange medium in an external heat exchanger 1 ', c) expansion of the working medium and d) heat exchange between the working medium and a heat exchange medium in an internal heat exchanger 1' '. For this purpose, the compressor unit 23 has essentially radially extending compression channels 25, in which the working medium flows radially outward with respect to the axis of rotation 22. Due to the centrifugal acceleration, the working medium is compressed in the compression channels 25. Accordingly, the working medium for reducing the pressure in expansion channels 26 of the tensioning unit 24 is guided substantially radially inwards.
    The compressor unit 23 and the relaxation unit 24 are characterized by axial, i. in the direction of the axis of rotation 22, extending flow channels connected to each other, in which a heat exchange between the working medium and a Wärmeaustauschmedi¬um, for example water, takes place. For this purpose, outer heat exchangers 1 'and inner heat exchangers 1' are provided with respect to the rotation axis, which are substantially parallel to the rotation axis 22. When the device 20 is operated as a heat pump, the working medium compressed in the compression channels 25 emits heat in a heat exchange medium of a first, comparatively high temperature in the outer heat exchangers 1 '. The working medium, which has been expanded in the expansion channels 26, transfers heat from the heat exchange medium to a second, relatively high temperature. comparatively low temperature. Thus, the centrifugal acceleration acting on the working medium is exploited to produce different pressure levels or temperature levels. Heat of high temperature is withdrawn from the compressed working medium, and heat is supplied to the expanded working medium at a comparatively low temperature. In a drive of the device 20 as a motor, the flow channels are flowed through by the working medium in the reverse direction. Accordingly, the heat exchange changes, heat being supplied to the working medium at the outer heat exchanger 1 'and heat being removed from the working medium at the inner heat exchanger 1 ".
    As can be further seen from FIG. 1, a plurality of, in the illustrated embodiment, twelve, inner heat exchangers 1 'and a plurality of, in the embodiment shown, twelve, outer heat exchangers 1' are provided, which are arranged at regular angular intervals with respect to the axis of rotation. The inner heat exchangers 1 'and the outer heat exchangers 1' are each substantially parallel to the axis of rotation 22, wherein the compression and Ent¬ Entspannungskanäle 25 between the inner heat exchangers 1 'and the outer heat exchangers 1' extend.
    2, parts of the device 20 are shown in longitudinal section, with only one of the inner heat exchangers 1 "and one of the outer heat exchangers 1 'being shown. In addition, in Fig. 2, a paddle wheel 30 is seen, with which in the embodiment shown, the flow of the working medium is maintained about the axis of rotation 22. The impeller 30 is on the one hand connected to supply channels 31, which take over the working medium from the inner heat exchangers 1 ''. In addition, the paddle wheel 30 is connected to discharge channels 32, with which the working medium is guided into the compression channels 25 of the compressor unit 23. The compression channels 25 are connected to the outer heat exchanger 1 '.
    As can be seen from FIG. 2, the supply ducts 31 have outlet sections 34 which extend essentially parallel to the axis of rotation 22 and extend directly in front of an inlet opening 33 of the blade wheel 30, so that the flows of the working medium in the supply channels 31 are separated from one another and in the direction of flow ¬sentlichen be led parallel to the axis of rotation 22 in the paddle wheel 30.
    As is further apparent from FIG. 2, the supply ducts 31 have feed sections 35 running essentially in the radial direction, which are arranged between the outlet sections 34 opening into the blade wheel 30 and the inner heat exchangers 1 ''. The discharge channels 32 are connected to the Ver¬dichtungskanälen 25, which lead the working fluid to the outer heat exchangers 1 '.
    As is further apparent from FIG. 2, the impeller 30 is arranged closer to the rotational axis 22 in the radial direction than the inner heat exchanger 1 ". In the embodiment shown, the rotational axis of the blade wheel 30 is arranged in alignment with the axis of rotation 22 of the rotor 21, in order to reduce the stresses due to the centrifugal acceleration on the bearing of the shaft of the blade wheel 30.
    FIG. 2 a shows a temperature (T) - entropy (S) diagram, where the individual states of the working medium are denoted by Z 1 to Z 7. In FIG. 2, the positions inside the device 20 are correspondingly marked, at which the working medium substantially reaches the states ZI to Z7. Thus, in operation as a heat pump, the following process steps are performed (in a heat engine operation, the reverse cycle would be performed): - 1 to 2: substantially isentropic compression due to the maximum rotation from the radius ZI of the near-axis heat exchanger 1 "to the radius Z2 the off-axis heat exchanger 1 '; 2 to 3: essentially isobaric heat removal from the working medium to the heat exchange medium in the outer heat exchanger 1 'at a comparatively high temperature and at a constant radius of the flow; 3 to 4: substantially isentropic expansion due to the maximum rotation from the radius of the outer heat exchanger 1 'to the radius of the inner heat exchanger 1' '; 4 to 5: essentially isobaric heat removal at comparatively low temperature at a constant radius in the inner heat exchanger 1 "; 5 to 6: essentially isentropic expansion due to the main rotation from the radius of the inner heat exchanger to the entry radius of the impeller; - 6 after 7: compression inside the paddle wheel, the losses causing an increase in entropy; and - 7 to 1: essentially isentropic compression due to the main rotation from the exit of the impeller to the radius of the state ZI.
    As can be seen in particular from FIG. 3, the supply ducts 31 at the outlet sections 34 have arcuately curved walls 36 which effect a deflection of the working medium by substantially 90 ° from the radial inlet sections 35 into the axial outlet sections 34.
    As can be seen in particular from FIG. 4, the outlet sections 34 of the supply channels 31 are delimited by separating elements 37 which extend substantially in radial and axial direction to the axis of rotation 22 and which are formed in the embodiment shown by substantially planar partitions. The Trennele¬mente 37 have a radial extent and are arranged star-shaped. In the embodiment shown, the outlet sections 34 are therefore arranged regularly and at constant radial intervals around the axis of rotation 22 of the rotor 21.
    It is further apparent from FIG. 4 that the paddle wheel 30 has a plurality of arcuately curved blades 38, with which the working medium is accelerated in the direction of rotation 39 of the paddle wheel 30 as it flows through the paddle wheel 30. The impeller 30 has, on the side facing the rotation axis 22, a radial section 40 free of blades 39, in which the flows of the working medium from the supply channels 31 are brought together and homogenized. Provided on the radial section 40 is an arcuately curved deflection wall 41 (see FIG. 3) with which the working medium is deflected by at least 90 ° from the axial flow on entering the blade wheel 30 into a radial flow in front of the blades 39.
    As can be seen in Fig. 4, the discharge channels 32 have an envelope of the impeller 30, i. with respect to the outer surface of the blade wheel 30, which is circular in cross-section, inlet sections 42, which run inclined to the radial direction, and which are connected to discharge sections 43 extending essentially in the radial direction.
    As can be seen schematically in Figures 4, 6, the paddle wheel 30 has a paddlewheel shaft 44 connected to a motor (not shown). The motor is configured to rotate the impeller 30 in the direction of rotation 45 of the rotor 21. In the embodiment shown, the axis of rotation of the impeller 44 and the axis of rotation 22 of the rotor 21 coincide. In Be¬trieb as a heat engine, a generator is connected to the paddle wheel 30, which then works as a turbine. The turbine converts a differential pressure into wave power when it flows through with a corresponding mass flow.
    As can be seen in FIG. 5, the device 20 has dynamic sealing gaps 46 which are intended to minimize backflows due to an increased pressure at the outlet of the blade wheel 30 in relation to the inlet. In the sealing gaps 46 engage Gegenlamellen47 of the paddle wheel 30 in order to produce several small gaps as possible.
    7 shows an alternative embodiment in which the individual blade wheel 30 has a plurality of paddlewheel stages 30 ', 30 "which can be flowed through one behind the other in the embodiment shown. The Schaufelradstufen 30 ', 30' 'are connected to each other via a deflection 30' '', with which the working fluid from a flow radially outward after the first Schaufelradstufe 30 '' first radially into a flow after and then into a flow in Each impeller stage 30 ', 30' 'is constructed in accordance with the single-stage embodiment according to FIGS. 1 to 6. In the embodiment shown, the paddlewheel stages 30 ', 30 "are disposed on the same sprocket shaft 44, which is connected to a motor or to a generator. The paddlewheel stages 30 ', 30 "may alternatively be supported on separate paddlewheel shafts, with each paddlewheel stage 30', 30" connected to a motor or generator.
    权利要求:
    Claims (18)
    [1]
    Claims 1. A device (20) for converting thermal energy of low temperature into thermal energy of higher temperature by means of mechanical energy and vice versa with a rotor (21) rotatably mounted about a rotation axis (22) for a working medium passing through a closed cycle process, wherein Rotor (21) a compressor unit (23) with a plurality of compression channels (25) in which flows of the working medium for increasing the pressure with respect to the axis of rotation (22) can be guided substantially radially outwardly, and a relaxation unit (24) with a plurality of relaxation channels (26 ), in which flows of the Arbeitsmedi¬ums for pressure reduction with respect to the axis of rotation (22) are generally radially inwardly feasible, wherein the rotor (21) further heat exchanger (1 ', 1' ') for a Wärmeaus¬ exchange between the working medium and a heat exchange medium, and with a relative to the rotor (21) rotatable impeller (30), we In a heat pump operating state for maintaining the flows of the working medium about the axis of rotation (22) of the rotor (21) and / or in a generator driving state for utilizing the flow energy of Arbeitsmedi¬ums is provided, characterized in that the paddle wheel (30) between in the heat pump operating state the flow of the working medium supplying supply channels (31) and at least one in the heat pump operating state, the flow of Arbeitsme¬diums dissipating discharge channel (32) of the rotor (21) angeord¬net is, wherein the supply channels (31) substantially parallel to the axis of rotation ( 22) extending until immediately in front of an inlet opening (33) of the impeller (30) have outlet portions (34), so that individual flows of the working medium from the feed channels (31) substantially parallel to the axis of rotation (22) in the paddle wheel (30) are feasible ,
    [2]
    Device (20) according to claim 1, characterized in that the supply ducts (31) have substantially radially extending supply line sections (35) which are arranged between the exit sections (34) and with respect to the axis of rotation (22) of internal heat exchangers ( ! '') are arranged.
    [3]
    3. Device (20) according to claim 1 or 2, characterized gekennzeich¬net that the at least one discharge channel (32) with the Ver¬dichtungskanälen (25) is connected, which with respect to the rotational axis (22) outer heat exchangers (1 '. ) are connected.
    [4]
    Device (20) according to claim 2 or 3, characterized in that the impeller (30) is arranged in the radial direction closer to the axis of rotation (22) than the inner heat exchanger (1 ''), the impeller (30) being preferred is arranged concentrically about the axis of rotation (22) of the rotor (11).
    [5]
    5. Device (20) according to any one of claims 2 to 4, characterized in that the supply channels (31) at the Austritts¬abschnitten (34) arcuately curved walls (36), which a deflection of the working medium to substantially 90 ° of the Lead supply sections (35) into the outlet sections (34).
    [6]
    6. Device (20) according to one of claims 1 to 5, characterized in that the outlet sections (34) of the Zulei¬tungskanäle (31) between substantially in the radial and axia¬ler direction to the axis of rotation extending separating elements (37), in particular essentially planar partitions are formed.
    [7]
    7. Device (20) according to one of claims 1 to 6, characterized in that the impeller (30) has a plurality of ins¬besondere arcuately curved blades (38).
    [8]
    8. Device (20) according to one of claims 1 to 7, characterized in that the impeller (30) on the axis of rotation (22) facing side of a blades (38) free Radialab¬ section (40).
    [9]
    9. Device (20) according to claim 8, characterized in that the impeller (30) at the radial portion (40) has a bow-shaped curved deflection wall (41), with which the working medium by substantially 90 ° in the radial direction deflectable is.
    [10]
    10. Device (20) according to one of claims 1 to 9, characterized in that the at least one discharge channel (32) ei¬nen arranged obliquely to the radial direction inlet portion (42) which with a substantially radially extending discharge section (43 ) connected is.
    [11]
    11. Device (20) according to one of claims 1 to 10, characterized in that the impeller (30) has a particular pa¬rallel to the axis of rotation (22) of the rotor (21) rotatable Schaufel¬radwelle (44), which with a motor or connected to a generator.
    [12]
    A device (20) according to claim 9, characterized in that the motor for rotating the paddle wheel (30) in the same rotational direction (39, 45) as the rotor (21) with the expansion (25) and compression channels (26) for the Working medium is set up.
    [13]
    A device (20) according to any one of claims 1 to 12, characterized in that at least one outer heat exchanger (1 ') is provided with respect to the rotational axis of the first heat exchanger (1' ') and at least one external heat exchanger (1') with respect to the axis of rotation (22) in each case a plurality of inner heat exchangers (111) and outer heat exchanger (1 ') are provided.
    [14]
    14. Device (20) according to claim 13, characterized in that the number of inner heat exchangers (1 '') corresponds to a multiple of the outer heat exchanger (1 ') or vice versa.
    [15]
    15. Device (20) according to claim 13 or 14, characterized gekenn¬zeichnet that the at least one inner heat exchanger (1 '') and the at least one outer heat exchanger (1 ') are substantially pa¬rallel to the axis of rotation (22), wherein the compression (25) and / or expansion channels (26) between the inne¬ren heat exchanger (1 '') and the outer heat exchanger (1 ') run.
    [16]
    16. Device (20) according to any one of claims 1 to 15, characterized in that the impeller (30) has a plurality of successively behind of the working medium through-flow Schaufelradstufen (30 ', 30' ').
    [17]
    17. A method for converting low-temperature thermal energy into higher-temperature thermal energy by means of mechanical energy and vice versa, wherein a working medium in a rotating about an axis (22) rotating rotor (21) passes through a closed cycle, wherein a plurality of streams of Arbeitsme¬diums in order to increase the pressure in relation to the axis of rotation (22), they are generally guided radially outward, with the flows of the working medium being guided essentially radially inwards in order to reduce the pressure with respect to the axis of rotation, whereby a heat exchange between the working medium and a heat exchange medium is carried out, the working medium being guided in a heat pump operating state for maintaining the flows of the working medium about the axis of rotation of the rotor and / or in a generator operating state for utilizing the flow energy of the working medium through a paddle wheel (30), characterized the existence individual flows of the working medium in the heat pump operating state are led to immediately in front of the impeller (30) and introduced into the impeller (30) substantially parallel to the axis of rotation (22).
    [18]
    18. The method according to claim 17, characterized in that the impeller (30) in the same direction of rotation (39, 45) and with ei¬ner higher absolute speed as the rotor (21) with the Ent-voltage (25) and compression channels (26 ) is rotated.
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    同族专利:
    公开号 | 公开日
    US20170045270A1|2017-02-16|
    ES2684621T3|2018-10-03|
    PL3137821T3|2019-01-31|
    EP3137821B1|2018-05-23|
    DK3137821T3|2018-08-27|
    CN106415154A|2017-02-15|
    US10247450B2|2019-04-02|
    AT515217B1|2015-07-15|
    EP3137821A1|2017-03-08|
    CN106415154B|2019-04-30|
    JP2017514098A|2017-06-01|
    WO2015161330A1|2015-10-29|
    HUE038862T2|2018-12-28|
    JP6496010B2|2019-04-03|
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    法律状态:
    2020-12-15| MM01| Lapse because of not paying annual fees|Effective date: 20200423 |
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50296/2014A|AT515217B1|2014-04-23|2014-04-23|Apparatus and method for converting thermal energy|ATA50296/2014A| AT515217B1|2014-04-23|2014-04-23|Apparatus and method for converting thermal energy|
    US15/306,049| US10247450B2|2014-04-23|2015-04-22|Device and method for converting thermal energy|
    DK15724506.9T| DK3137821T3|2014-04-23|2015-04-22|Device and method for converting thermal energy|
    ES15724506.9T| ES2684621T3|2014-04-23|2015-04-22|Device and procedure for thermal energy conversion|
    CN201580029468.6A| CN106415154B|2014-04-23|2015-04-22|Device and method for converting thermal energy|
    PCT/AT2015/050098| WO2015161330A1|2014-04-23|2015-04-22|Device and method for converting thermal energy|
    JP2017507041A| JP6496010B2|2014-04-23|2015-04-22|Apparatus and method for converting thermal energy|
    HUE15724506A| HUE038862T2|2014-04-23|2015-04-22|Device and method for converting thermal energy|
    EP15724506.9A| EP3137821B1|2014-04-23|2015-04-22|Device and method for converting thermal energy|
    PL15724506T| PL3137821T3|2014-04-23|2015-04-22|Device and method for converting thermal energy|
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