For a heat exchanger, in particular a shell and tube heat exchanger, arranged in a rotor having a rotation axis

Abstract

The invention relates to a heat exchanger (7), in particular a shell and tube heat exchanger, for being arranged in a rotor (1) having a rotation axis (2), the heat exchanger comprising: a first heat exchange channel (15) for conducting a first heat exchange medium, in particular a liquid; a second heat exchange channel (12) for conducting a second heat exchange medium, in particular a gas, preferably an inert gas, wherein the second heat exchange channel (12) in the assembled state of use comprises at least one inner heat exchange channel closer to the rotation axis (2) and an outer heat exchange channel further away from the rotation axis (2); a distribution element (17) which expands in the flow direction of the second heat exchange medium, preferably in a conical shape, for feeding the second heat exchange medium from an inlet opening (17A) in the distribution element (17) to the second heat exchange channel (12). An inlet opening (29) in the heat exchange channel (12); a merging element (18) which tapers in the flow direction of the second heat exchange medium, preferably tapers substantially conically, for discharging the second heat exchange medium from the outflow opening (28) in the second heat exchange channel (12) to the outlet opening (18A) in the merging element (18); and a device (30) for homogenizing the flow through the second heat exchange channel (12), the device comprising a throttling member for throttling the internal flow of the second heat exchange medium through the internal heat exchange channel between the inlet opening (17A) in the distribution element (17) and the outlet opening (18A) in the merging element (18) to different degrees and the external flow of the second heat exchange medium through the external heat exchange channel.

Description

Technical Field

[0001] The present invention relates to a heat exchanger for use with a rotor having a rotation axis, in particular a shell and tube heat exchanger, comprising:

[0002] a first heat exchange channel for guiding a first heat exchange medium, in particular a liquid;

[0003] second heat exchange channels for conducting a second heat exchange medium, in particular a gas, preferably an inert gas, wherein the second heat exchange channels in the assembled use state of the heat exchanger comprise at least one inner heat exchange channel closer to the rotation axis and an outer heat exchange channel further away from the rotation axis;

[0004] a distribution element, which expands in the flow direction of the second heat exchange medium, preferably in a conical shape, for feeding the second heat exchange medium from an inlet opening in the distribution element to an inflow opening in the second heat exchange channel;

[0005] A merging element, which tapers in the flow direction of the second heat exchange medium, preferably tapers substantially conically, is used to discharge the second heat exchange medium from the outflow opening in the second heat exchange channel to the outlet opening in the merging element.

[0006] The present invention also relates to a rotor, in particular to a rotary heat pump, comprising:

[0007] Axis of rotation,

[0008] Heat exchanger.

[0009] Finally, the invention relates to a method for exchanging heat between a first heat exchange medium, in particular a liquid, and a second heat exchange medium, in particular a gas, preferably an inert gas, inside a rotor, comprising the following steps:

[0010] rotating the rotor about a rotation axis;

[0011] directing the first heat exchange medium along a first heat exchange channel of the heat exchanger;

[0012] A second heat exchange medium is guided along second heat exchange channels of the heat exchanger at different distances from the rotational axis of the rotor. Background Art

[0013] A rotary heat pump is known from WO 2015 / 103656, in which the centrifugal acceleration of the rotor is used to generate different pressure or temperature levels. Here, high-temperature heat is extracted from the compressed working medium, and relatively low-temperature heat is supplied to the expanded working medium. To this end, the rotary heat pump comprises an internal heat exchanger and an external heat exchanger, which are arranged substantially parallel to the axis of rotation of the rotor. The internal heat exchanger is configured to perform heat exchange at a lower temperature, and the external heat exchanger is configured to perform heat exchange at a higher temperature.

[0014] In stationary applications, shell and tube heat exchangers are often used, in which the working medium flows through a bundle of tubes arranged in a cylindrical housing shell. The heat exchange medium flows through the housing space in a circuit formed by baffles. This type of heat exchanger ensures a particularly good heat transfer between the two media. In stationary applications of such shell and tube heat exchangers, the inlet flow of the working medium is divided symmetrically with respect to the main flow direction in order to distribute the working medium accordingly between the individual tubes.

[0015] However, when attempts were made to use known shell and tube heat exchangers with a rotor, in particular with a rotary heat pump, it has been shown that the heat transfer between the media is significantly lower than expected.

[0016] GB 1 383 690 A and CH 576 615 A5 further illustrate the general state of the art. Summary of the invention

[0017] It is therefore an object of the present invention to mitigate or eliminate the disadvantages of the prior art.It is an object of the present invention to preferably provide a heat exchanger which has a high efficiency when used with a rotor.

[0018] This object is achieved by a heat exchanger according to claim 1, a rotor according to claim 8 and a method according to claim 13. Preferred embodiments are given in the dependent claims.

[0019] According to the present invention, a device for homogenizing the flow through the second heat exchange channel is provided. The device comprises a throttling member designed to throttle the inflow of the second heat exchange medium through the inner heat exchange channel in the second heat exchange channel and the outflow of the heat exchange medium through the outer heat exchange channel in the second heat exchange channel between the inlet opening in the distribution element and the outlet opening in the merging element to different degrees.

[0020] For the purposes of this disclosure, position and direction indications refer to the intended use of the heat exchanger as part of a rotor. "Upstream" and "downstream" refer to the flow direction of the second heat exchange medium. "Radial" and "axial" refer to the axis of rotation of the rotor. "Inboard" means closer to the axis of rotation of the rotor. "Outboard" means farther from the axis of rotation. Distance refers to the radial distance from the axis of rotation.

[0021] The invention is therefore based on the surprising finding that a heat exchanger cannot be operated efficiently under the effect of centrifugal acceleration by uniformly distributing the second heat exchange medium. The invention solves this problem in that different pressure differences of the side flows of the second heat exchange medium flowing at different distances from the axis of rotation between the inlet opening in the distribution element and the outlet opening in the merging element are at least partially, preferably substantially completely, compensated.

[0022] Advantageously, this may achieve a substantially uniform flow through the second heat exchange channel.

[0023] Comprehensive flow analysis shows that the main reason for the different pressure differences of the side flows is that the external flow in the distribution element first flows outward and is compressed due to the action of centrifugal force, and then the external flow along the external heat exchange channel in the second heat exchange channel exchanges heat with the first heat exchange medium, and then flows inward in the merging element toward the outlet opening and expands thereby; for the internal flow, the order is opposite, because the internal flow in the distribution element first flows inward and expands due to the action of centrifugal force, and then exchanges heat with the first heat exchange medium along the internal heat exchange channel in the second heat exchange channel, and then the internal flow in the merging element is guided outward toward the outlet opening and is compressed thereby.

[0024] When the second heat exchange medium in the second heat exchange channel releases heat to the first heat exchange medium, a pressure difference is first generated by compression at low density before heat exchange, that is, the second heat exchange medium flows from the collection through the inlet opening to the inlet opening in the external heat exchange channel, and then heat is dissipated in the external heat exchange channel, whereby the temperature of the second heat exchange medium decreases, and therefore - in the case of substantially isobaric heat exchange - the density increases; then the second heat exchange medium expands again at a higher density, that is, the second heat exchange medium flows from the outflow opening in the external heat exchange channel to the collection at the outlet opening. Since the second heat exchange medium compresses at low density (low pressure difference) and expands at high density (higher pressure difference), when considering this streamline, there will be an additional pressure difference, which is required when flowing through the external heat exchange channel. This will cause the second heat exchange medium to favor the internal heat exchange channel in the second heat exchange channel. When heat is supplied to the second heat exchange medium by the first heat exchange medium, the situation is reversed. Then, the second heat exchange medium will favor the external heat exchange channel in the second heat exchange channel.

[0025] The invention now sets out to compensate for the additional pressure difference by means of a throttle component which throttles the outflow and the inflow in the section between the inlet opening in the distribution element and the outflow opening in the merging element to different degrees, ie results in different flow resistances.

[0026] If heat dissipation from the second heat exchange medium to the first heat exchange medium occurs in the second heat exchange channel, the throttling member is configured to throttle the inner flow to a greater extent than the outer flow.

[0027] If heat supply from the first heat exchange medium to the second heat exchange medium occurs in the second heat exchange channel, the throttling member is configured to throttle the external flow to a greater extent than the internal flow.

[0028] Thus, the throttling means is configured to throttle the flow of the second heat exchange medium asymmetrically with respect to a center or symmetry axis of the heat exchanger. By means of the throttling means, the second heat exchange medium is subjected to substantially the same pressure difference as it flows through the heat exchanger from the inlet to the outlet opening. Advantageously, in this way, a substantially uniform flow through the second heat exchange channels can be achieved, so that the second heat exchange medium along the second heat exchange channels comprises in each case substantially the same average flow velocity or substantially the same volume flow rate (provided that, preferably, the second flow channels have the same flow cross section).

[0029] In a preferred embodiment, the heat exchanger is designed as a shell and tube heat exchanger. The shell and tube heat exchanger comprises a tube bundle with a plurality of tubes, preferably each tube having a substantially circular cross section, which surround the second heat exchange channel. The tubes preferably extend parallel to each other. The tube bundle can be arranged in a preferably cylindrical housing. The first heat exchange medium is guided through the first heat exchange channel extending inside the housing. Deflection elements for the first heat exchange medium are preferably arranged in the housing. The deflection elements are preferably arranged substantially perpendicular to the tubes. Preferably, the deflection elements inside the housing leave recesses for the first heat exchange medium, wherein the recesses are preferably arranged alternately on opposite sides. As a result, the first heat exchange medium is guided through the interior of the housing in a loop, wherein the first heat exchange medium flows part by part transversely to the tubes with the second heat exchange channel.

[0030] In a first preferred embodiment, the throttling device comprises a throttling orifice plate having a throttling opening, wherein the throttling opening further away from the axis of rotation and the throttling opening closer to the axis of rotation have different sizes. The throttling orifice plate can be arranged upstream of the inflow opening, in particular directly upstream of the inflow opening, or arranged downstream of the outflow opening, in particular directly downstream of the outflow opening. In an embodiment for dissipating heat from the second heat exchange medium, the throttling opening further away from the axis of rotation is larger than the throttling opening closer to the axis of rotation. In an embodiment for supplying heat to the second heat exchange medium, the throttling opening further away from the axis of rotation is smaller than the throttling opening closer to the axis of rotation. The advantage of this embodiment of the throttling component is that the structure is simple to implement. In addition, the heat exchanger can be set to a specific operating point by simply replacing the throttling orifice plate.

[0031] The throttling orifice plate is preferably arranged upstream of the second heat exchange channel so that the second heat exchange medium is respectively supplied to exactly one of the second heat exchange channels through the throttling opening. Alternatively, the throttling orifice plate can be arranged downstream of the second heat exchange channel so that the second heat exchange medium is discharged from each second heat exchange channel through exactly one throttling opening.

[0032] Preferred embodiments of the throttling orifice are described below with reference to an embodiment for dissipating heat to the second heat exchange medium along the second heat exchange channel. Thus, if a greater degree of throttling is provided by the distance outward from the axis of rotation (in this case by means of a smaller throttling opening), the principle can be transferred to the case of supplying heat to the second heat exchange medium.

[0033] The throttling orifice preferably comprises at least one first throttling opening at a first distance from the axis of rotation and at least one second throttling opening at a second distance from the axis of rotation of the rotor, the second distance being greater than the first distance and the second throttling opening being greater than the first throttling opening. The throttling orifice preferably comprises at least one third throttling opening at a third distance from the axis of rotation, the third distance being greater than the second distance, the at least one third throttling opening being greater than the at least one second throttling opening. The throttling orifice preferably comprises at least one fourth throttling opening at a fourth distance from the axis of rotation, the fourth distance being greater than the third distance, the at least one fourth throttling opening being greater than the at least one third throttling opening. Of course, the throttling orifice may comprise further throttling openings at a greater distance from the axis of rotation of the rotor, wherein the throttling openings further away from the axis of rotation are in each case greater than the throttling openings closer to the axis of rotation.

[0034] In a preferred embodiment, the heat exchanger comprises a plurality of rows of second heat exchange channels, each row of second heat exchange channels having substantially the same distance from the rotation axis of the rotor. Accordingly, the throttling orifice plate preferably comprises a plurality of rows, each row having a plurality of throttling openings, wherein the row further away from the rotation axis and the row closer to the rotation axis comprise throttling openings of different sizes. In the case of heat dissipation, the row of throttling openings further away from the rotation axis comprises larger throttling openings than the row of throttling openings closer to the rotation axis.

[0035] Thus, a first row of first throttle openings may be provided, each being at a substantially first distance from the axis of rotation, and a second row of second throttle openings, each being at a substantially second distance from the axis of rotation, preferably a third row of third throttle openings, each being at a substantially third distance from the axis of rotation, preferably a fourth row of fourth throttle openings, each being at a substantially fourth distance from the axis of rotation, preferably at least another row of further throttle openings, each being at a further distance from the axis of rotation.

[0036] In order to enable the second heat exchange medium to be supplied to each second heat exchange channel, the distribution element is arranged upstream of the second heat exchange channel (in the flow direction of the second heat exchange medium), and the distribution element is expanded, that is, formed with a cross section that increases in the flow direction of the second heat exchange medium. The distribution element enables the flow of the second heat exchange medium at the inlet of the heat exchanger to be distributed to the individual flows in the second heat exchange channels. Preferably, the distribution element expands in a conical shape.

[0037] In a second preferred embodiment, a flow grid is arranged in the distribution element, the flow grid comprising individual distribution channels expanding in the flow direction, each distribution channel comprising an initial portion and an end portion.

[0038] In a second embodiment of the throttling member, the initial part and / or the end part of the distribution channel farther from the axis of rotation and the initial part and / or the end part of the distribution channel closer to the axis of rotation include different flow cross sections. The advantage of this embodiment is that the flow grid is generally useful for good distribution and flow guidance in order to keep the pressure loss as low as possible. Advantageously, the flow grid can now also be designed as a throttling member, with which an asymmetric cross-sectional expansion is achieved in order to compensate for different pressure differences depending on the distance from the axis of rotation. The initial part is connected to the inlet of the heat exchanger. The end part guides the second heat exchange medium to the inflow opening in the second heat exchange channel. In the case of dissipating heat from the second heat exchange medium to the first heat exchange medium, the initial part and / or the end part of the distribution channel farther from the axis of rotation include a larger flow cross section than the initial part and / or the end part of the distribution channel closer to the axis of rotation.

[0039] The flow grid preferably comprises exactly one distribution channel per second heat exchange channel, so that the second heat exchange medium is supplied to exactly one second heat exchange channel in the second heat exchange channels via each distribution channel. The distribution channels are separated from one another by individual wall parts, wherein preferably vertical wall parts and horizontal wall parts are provided. The vertical wall parts serve on the one hand to ensure a uniform distribution in the tangential direction (so that the above-mentioned problem of different pressures does not arise here), and also have the advantage that the horizontal wall parts provided for the radial distribution of the flow are supported against deflection under the action of centrifugal forces.

[0040] The preferred embodiment of the flow grid will be described below in conjunction with an embodiment of dissipating heat to the second heat exchange medium along the second heat exchange channel.Thus, if the distance outward from the axis of rotation provides a greater degree of throttling, the principle can be transferred to the case of providing heat.

[0041] The flow grid preferably comprises at least one first distribution channel at a first distance from the axis of rotation and at least one second distribution channel at a second distance from the axis of rotation of the rotor, the second distance being greater than the first distance, and the initial portion and / or the terminal portion having a larger flow cross section than the initial portion and / or the terminal portion of the first distribution channel. Preferably, the flow grid comprises at least one third distribution channel at a third distance from the axis of rotation, the third distance being greater than the second distance, and the initial portion and / or the terminal portion of the third distribution channel having a larger flow cross section than the initial portion and / or the terminal portion of the second distribution channel. Preferably, the flow grid comprises at least one fourth distribution channel at a fourth distance from the axis of rotation, the fourth distance being greater than the third distance, and the initial portion and / or the terminal portion of the fourth distribution channel having a larger flow cross section than the initial portion and / or the terminal portion of the third distribution channel. Of course, the flow grid may comprise further distribution channels at a greater distance from the axis of rotation, wherein the flow cross section of the initial portion and / or the terminal portion increases with the distance from the axis of rotation.

[0042] The flow grid preferably comprises: at least one first row, which has a plurality of separate, i.e. separated first distribution channels at a substantially first distance from the rotation axis, and a second row, which has a plurality of second distribution channels at a substantially second distance from the rotation axis, preferably also a third row, which has a plurality of third distribution channels at a substantially third distance from the rotation axis, preferably also a fourth row, which has a plurality of fourth distribution channels at a substantially fourth distance from the rotation axis, and preferably also additional rows, each additional row having a plurality of additional distribution channels.

[0043] In a first variant, the initial part of the distribution channel further away from the axis of rotation comprises a larger flow cross section than the initial part of the distribution channel closer to the axis of rotation, wherein the end part of the distribution channel further away from the axis of rotation comprises essentially the same flow cross section as the end part of the distribution channel closer to the axis of rotation. This embodiment is particularly advantageous for structural reasons if the second heat exchange channels have the same flow cross section. Thus, in this variant, the second heat exchange medium can flow into the flow grid asymmetrically, wherein during the inflow, the flow cross section increases with the distance from the axis of rotation. On the other hand, the outflow from the flow grid can occur symmetrically, i.e. with essentially the same flow cross section.

[0044] In a second variant, the end portion of the distribution channel further away from the axis of rotation comprises a larger flow cross section than the end portion of the distribution channel closer to the axis of rotation, wherein the initial portion of the distribution channel further away from the axis of rotation comprises substantially the same flow cross section as the initial portion of the distribution channel closer to the axis of rotation. The structure of this embodiment is particularly simple. Thus, in this variant, the inflow into the flow grid can be symmetrical, but the outflow from the flow grid can be asymmetrical.

[0045] In a third variant, both the initial and terminal portions of the distribution channel further away from the axis of rotation comprise a larger flow cross section than the initial and terminal portions of the distribution channel closer to the axis of rotation. Thus, in this variant, both the inflow into the flow grid and the outflow from the flow grid can occur asymmetrically, i.e. with a larger flow cross section as the distance from the axis of rotation increases.

[0046] The asymmetrical distribution of the second heat exchange medium through the flow grid causes the second heat exchange medium to flow partially through a smaller flow cross section than the axially distal flow of the second heat exchange medium from entering the heat exchanger until leaving the heat exchanger, whereby the axially approaching flow is subjected to a higher pressure loss than the axially distal flow. As a result, the pressure difference between the axially approaching second heat exchange channel and the axially distal second heat exchange channel is at least partially, preferably substantially completely, compensated.

[0047] In addition, a flow grid may be arranged in the merging element, the flow grid comprising individual merging channels tapering in the flow direction in the merging element, each merging channel comprising an initial portion (on the side of the outflow opening in the second heat exchange channel) and an end portion (on the side away from the outflow opening). In order to form a throttling member, the initial portion and / or the end portion of the merging channel further away from the rotation axis and the initial portion and / or the end portion of the merging channel closer to the rotation axis comprise different flow cross sections.

[0048] In a third preferred embodiment, the means for homogenizing the flow through the second heat exchange channel comprises turbulators, in particular spiral turbulators, within the second heat exchange channel, wherein turbulators further away from the axis of rotation and turbulators closer to the axis of rotation result in different pressure losses. In the case of heat dissipation from the second heat exchange medium along the second heat exchange channel, turbulators further away from the axis of rotation produce lower pressure losses than turbulators closer to the axis of rotation.

[0049] To this end, turbulators further from the rotation axis and turbulators closer to the rotation axis may include different spiral lengths. In the case of dissipating heat from the second heat exchange medium along the second heat exchange channel, turbulators further from the rotation axis may include a greater slope than turbulators closer to the rotation axis.

[0050] Compared with the aforementioned embodiments of the throttling device, the advantage of the turbulator is that not only can the pressure loss in the second heat exchange channel be adjusted to different degrees at different distances from the rotation axis to achieve a uniform flow through the second flow channel, but also the heat transfer is increased by the increased turbulence during heat transfer.

[0051] In the fourth embodiment, the outer heat exchange channel and the inner heat exchange channel in the second heat exchange channel for forming the throttling member include different flow cross sections, and have different diameters in the case of a tube having a circular cross section.

[0052] In a preferred application, a rotor, in particular a rotary heat pump, is provided with a heat exchanger according to one of the above-described embodiments.

[0053] In a first preferred embodiment, the central axis or the axis of symmetry of the heat exchanger is arranged at a radial distance from the axis of rotation, ie axially offset.

[0054] In a second preferred embodiment, the central axis of the heat exchanger is arranged to be substantially consistent with the rotation axis. In this case, the second heat exchange channels have different distances from the rotation axis.

[0055] In the rotor, the second heat exchange channels preferably extend substantially parallel to the axis of rotation and at different radial distances therefrom.The first heat exchange channels may extend in a cross section substantially perpendicular to the second heat exchange channels, as is common for shell and tube heat exchangers.

[0056] In a preferred embodiment, the rotor comprises a compression unit, in which the second heat exchange medium is directed away from the rotation axis due to centrifugal force to increase the pressure, and an expansion unit, in which the second heat exchange medium is directed towards the rotation axis due to centrifugal force to reduce the pressure.

[0057] In this embodiment of the rotor, preferably at least one internal heat exchanger relative to the rotation axis and at least one external heat exchanger relative to the rotation axis are provided. According to an embodiment, the external heat exchanger and / or the internal heat exchanger may be configured according to any of the above-described embodiments of the heat exchanger.

[0058] The method according to the invention for exchanging heat between a first heat exchange medium, in particular a liquid, and a second heat exchange medium, in particular a gas, preferably an inert gas, inside a rotor comprises the following steps:

[0059] rotating the rotor about the axis of rotation;

[0060] directing a first heat exchange medium along a first heat exchange channel of the heat exchanger,

[0061] directing a second heat exchange medium along second heat exchange channels of the heat exchanger at different distances from the axis of rotation of the rotor,

[0062] The flow through the second heat exchange channel is homogenized by throttling the inner flow of the second heat exchange medium closer to the rotation axis and the outer flow of the second heat exchange medium farther from the rotation axis to different degrees.

[0063] In a preferred embodiment, heat dissipation from the second heat exchange medium to the first heat exchange medium is performed along the second heat exchange channel, wherein the inflow of the second heat exchange medium is throttled to a greater extent than the outflow of the second heat exchange medium. DETAILED DESCRIPTION

[0064] The invention is explained below with reference to preferred exemplary embodiments shown in the drawings.

[0065] Figure 1 A rotor 1 is shown, which in the embodiment shown is implemented as a device for converting mechanical energy into thermal energy (or vice versa). The device is operated in particular as a rotary heat pump. The rotor 1 comprises an axis of rotation 2, which is horizontal, for example, during operation, and about which the rotor 1 rotates by means of an electric motor (not shown). The rotor 1 comprises a compression unit 3, in which the working medium is directed away from the axis of rotation 2 due to centrifugal force in order to increase the pressure. In addition, the rotor 1 comprises an expansion unit 4, in which the working medium is directed toward the axis of rotation 2 in order to reduce the pressure. The working medium is preferably directed in a closed loop within the rotor 1. In addition, the rotor 1 comprises a plurality of internal heat exchangers 5 (low-pressure heat exchangers) and a plurality of external heat exchangers 6 (high-pressure heat exchangers). In the internal heat exchangers 5 and the external heat exchangers 6, heat exchange is performed between a first heat exchange medium and a second heat exchange medium (i.e., a working medium). For example, such a device is shown in WO2015 / 103656, but with different types of heat exchangers.

[0066] Figure 2A A heat exchanger 7, also referred to as a heat transfer system, is shown in an embodiment which can be realized with an internal heat exchanger 5 and / or an external heat exchanger 6. The heat exchanger 7 is described below by way of example for use as an external heat exchanger 6, i.e. as a high-pressure heat exchanger. The heat exchanger 7 comprises an inlet element 8, via which a second heat exchange medium, i.e. a working medium, is supplied to the heat exchanger 7, and an outlet element 9, via which the second heat exchange medium leaves the heat exchanger 7.

[0067] In the embodiment shown, the heat exchanger 7 is designed as a shell and tube heat exchanger. The shell and tube heat exchanger comprises a cylindrical housing 10 in which a tube bundle is arranged. The tube bundle comprises elongated tubes 11 which are arranged parallel to each other and spaced apart in the radial direction and in the circumferential direction. Inside, the tubes 11 comprise second heat exchange channels 12 for a second heat exchange medium. The tubes 11 are each held at opposite ends in a tube sheet in the form of a bottom plate 11A (see Figure 2B ). The first heat exchange medium is guided to the interior of the housing 10 via a supply line 13 and, after heat exchange with the second heat exchange medium, is discharged from the housing 10 via a discharge line 14. Inside the housing 10, the first heat exchange medium flows in a first heat exchange channel 15, which is formed by means of a deflection element 16 so that the first heat exchange medium flows alternately in opposite directions transversely to the tube 11, i.e., alternately downward and upward in the position shown. Meanwhile, the first heat exchange medium is deflected into the next channel by the deflection element 16.

[0068] from Figure 2A It can also be seen that between the inlet element 8 and the inlet side of the housing 10, the heat exchanger 7 comprises a distribution element 17 with an inlet opening 17A, wherein the distribution element expands in the flow direction of the second heat exchange medium. In addition, between the outlet element 9 and the outlet side of the housing 10, the heat exchanger 7 comprises a merging element 18 with an outlet opening 18A for merging the individual flows of the second heat exchange medium after flowing through the second heat exchange channel 12. The merging element 18 tapers in the flow direction of the second heat exchange medium.

[0069] Figure 2B The heat exchanger 7 is shown in simplified form, wherein arrows illustrate the inflow and distribution of gas to the various second heat exchange channels 12 within the housing 10 .

[0070] In principle, an embodiment of the heat exchanger 7 as a shell and tube heat exchanger is very advantageous for use with the rotor 1. However, it is important that the flow through the second heat exchange channels 12 is uniform in order to efficiently utilize the heat transfer surface.

[0071] from Figure 3It can be seen that the flow of the second heat exchange medium entering the heat exchanger 7 is evenly distributed among the separate second flow channels 12 (i.e. the tubes of the tube bundle) by means of flow splitting, see arrows 20. To this end, a flow grid 21 can be arranged in the distribution element 17, which includes individual distribution channels 22 extending continuously along the flow grid 21. Figure 3 , the distribution channels 22 are designed identically in order to achieve uniform distribution.

[0072] However, surprisingly, it has been shown that, in the rotating state of the rotor 1 at high centrifugal acceleration, a number of phenomena occur which prevent the achievement of a uniform flow by simply dividing the incoming flow of the second heat exchange medium. As a reason, it has been recognized that during the entry and exit of the second heat exchange medium (in this case, gas), different densities occur at different radial distances from the center of rotation in the discrete second flow channels 12.

[0073] As shown in the schematic diagram when the reference heat exchanger 7 is used as the external (high pressure) heat exchanger 6, Figure 4 As can be seen in the figure, heat is intended to be transferred during operation from the second heat exchange medium, hereinafter also referred to as gas, to the first heat exchange medium, hereinafter also referred to as liquid or water. On the right, the inflow occurs at a relatively high temperature, while on the left, after the heat transfer, the outflow occurs at a relatively low temperature. This results in a higher density on the outflow side than on the inflow side.

[0074] In order to illustrate the technical effect, the following assumptions and simplifications are made in the model calculation:

[0075] Average radius of rotation axis: 900mm

[0076] Radial extension of the heat exchanger 7 (from the innermost second heat exchange channel 12 to the outermost heat exchange channel 12): 100 mm

[0077] Average pressure in heat exchanger: 120 bar

[0078] Average temperature 400K

[0079] Gas: Krypton

[0080] If an ideal gas flow is assumed, i.e., real gas properties are not considered, only gravitational acceleration occurs, and the heat exchanger is oriented so that the gravitational acceleration has the same direction as the centrifugal acceleration, then the pressure difference between the outermost flow channel and the innermost flow channel is 0.14 mbar, which is not considered due to its minimal effect.

[0081] Figure 5 shows a roughly calculated pressure difference between the flow channels (“on the outside” – Figure 4Arrow 23 in the middle; "on the inside" - Figure 4 The arrows 24 in FIG. 1 ), in revolutions per minute (rpm), illustrate the effect of the rotation on the heat exchanger 7 . The radial distance of the outermost channel from the axis of rotation 2 is shown by the arrows 25 and the radial distance of the innermost channel from the axis of rotation 2 is shown by the arrows 26. The main direction of the gas flow is indicated by the arrows 27. At a speed of 1,800 rpm of the rotor 1 , this pressure difference is 0.46 bar, which is therefore about 3,300 times greater than at gravitational acceleration (corresponding to the ratio of the accelerations). Therefore, if no other measures are taken, the gas will favor the inner channels, since the gas in the inner area will experience an increase in pressure, while the gas passing through the outermost channels will experience a decrease in pressure. In addition, a backflow may also occur, so that the gas flows from right to left on the inside and from left to right on the outside. As a result, more flow energy is required and a smaller effective heat exchanger surface is available, since in most cases only the inner area of ​​the heat exchanger is used.

[0082] Figure 6 and Figure 7 A first embodiment of a heat exchanger 7 according to the invention is shown for use in the context of an external heat exchanger 6 , with only the differences to the preceding embodiments being described below.

[0083] In this exemplary embodiment, a device 30 for homogenizing the flow through the second heat exchange channels 12 is provided, by which different pressure differences of the second heat exchange medium caused by the different radial distances of the second heat exchange channels 12 from the rotation axis 2 of the rotor 2 are compensated.

[0084] In the illustrated embodiment, throttling means for throttling the separate second heat exchange channels 12 to different degrees are provided as means 30 for homogenizing the flow through the second heat exchange channels 12. In this case, the flow of the second heat exchange medium closer to the rotation axis 2 (i.e., including a smaller radial distance) is throttled to a greater extent than the flow of the second heat exchange medium farther from the rotation axis 2 (i.e., including a larger radial distance).

[0085] In accordance with Figure 6 and Figure 7 In the embodiment of the present invention, the throttling device comprises a disc-shaped throttling orifice plate 31 which is circular in the flow direction of the second heat exchange medium and has a plurality of circular throttling openings 32, which are arranged directly upstream of the inflow opening 29 in the second heat exchange channel 12. The throttling openings 32 are arranged in rows, wherein the diameter of the throttling openings 32 increases from row to row outwards (i.e. away from the rotation axis 2). Within a row, the throttling openings 32 have the same diameter.

[0086] In accordance with Figure 8In the embodiment of the invention, a flow grid 21 of asymmetric design (relative to the central axis 36 of the heat exchanger 7) is provided as a means 30 for homogenizing the flow through the second heat exchange channel. The distribution channels 22 of the flow grid 21 each have an initial portion 22A and an end portion 22B. In the embodiment shown, the flow cross section of the initial portion 22A increases with the distance from the rotation axis 2. On the other hand, the end portion 22B has the same flow cross section. A central portion 22C extends between the initial portion 22A and the end portion 22B, the central portion 22C providing a continuous transition from the initial portion 22A to the end portion 22B.

[0087] In accordance with Fig. 9 In the embodiment of the present invention, the spiral turbulator 33 is inserted into the second heat exchange channel 12. In order to form the device 30, various spiral turbulators 33 are provided, so that the farther the spiral turbulator 33 is from the rotation axis 2, the lower the pressure loss of the second heat exchange medium. For this purpose, the spiral turbulator 33 farther away from the rotation axis 2 may include a larger spiral length (see arrow 34) compared to the turbulator 33 closer to the rotation axis 2 (see arrow 35).

[0088] List of reference numerals:

[0089] 1 Rotor

[0090] 2 Axis of rotation

[0091] 3 Compression unit

[0092] 4 Expansion unit

[0093] 5 Internal heat exchanger

[0094] 6 External heat exchanger

[0095] 7 Heat exchanger

[0096] 8 Inlet components

[0097] 9 Export components

[0098] 10. Housing

[0099] 11 Tube

[0100] 11A tube sheet

[0101] 12 Second heat exchange channel

[0102] 13 Supply lines

[0103] 14 Discharge line

[0104] 15. First heat exchange channel

[0105] 16 Deflection element

[0106] 17 Distribution components

[0107] 17A Entrance Opening

[0108] 18A Exit Opening

[0109] 18 Merge components

[0110] 20 Arrow

[0111] 21 Flow fence

[0112] 22 distribution channels

[0113] 22A Initial Section

[0114] 22B Central part

[0115] 22C terminal part

[0116] 23 Arrow

[0117] 24 Arrow

[0118] 25 Arrow

[0119] 26 Arrow

[0120] 27 Arrow

[0121] 28 Outflow opening

[0122] 29 Inflow opening

[0123] 30 Device for homogenizing the flow

[0124] 31 Orifice plate

[0125] 32 throttle opening

[0126] 33 Turbulator

[0127] 34 Arrow

[0128] 35 Arrow

[0129] 36 Central axis

Claims

1. A heat exchanger (7) for being arranged in a rotor (1) having a rotation axis (2), the heat exchanger comprising: A first heat exchange channel (15) for guiding a first heat exchange medium; A second heat exchange channel (12) for guiding a second heat exchange medium, wherein the second heat exchange channel (12) comprises, in an assembled state of use, at least one internal heat exchange channel closer to the rotation axis (2) and an external heat exchange channel farther from the rotation axis (2); a distribution element (17) extending in a flow direction of the second heat exchange medium and configured to feed the second heat exchange medium from an inlet opening (17A) in the distribution element (17) to an inlet opening (29) in the second heat exchange channel (12); a merging element (18) which tapers gradually along the flow direction of the second heat exchange medium and is used to discharge the second heat exchange medium from the outflow opening (28) in the second heat exchange channel (12) to the outlet opening (18A) in the merging element (18), The features include: The device (30) for homogenizing the flow through the second heat exchange channel (12) comprises a throttling member for throttling the inner flow of the second heat exchange medium through the inner heat exchange channel in the second heat exchange channel (12) and the outer flow of the second heat exchange medium through the outer heat exchange channel in the second heat exchange channel (12) to different degrees between the inlet opening (17A) in the distribution element (17) and the outlet opening (18A) in the merging element (18).

2. The heat exchanger (7) according to claim 1, characterized in that The throttling member comprises a throttling orifice plate (31) having a throttling opening (32), wherein the throttling opening (32) further away from the rotation axis (2) and the throttling opening (32) closer to the rotation axis (2) have different sizes.

3. The heat exchanger (7) according to claim 2, characterized in that The throttle orifice plate (31) has a plurality of throttle openings (32) arranged in rows, wherein a row further away from the rotation axis (2) and a row closer to the rotation axis (2) comprise throttle openings (32) of different sizes.

4. The heat exchanger (7) according to any one of claims 1 to 3, characterized in that The distribution element (17) comprises a flow grid (21) having respective distribution channels (22), wherein the distribution channels (22) expand in the flow direction of the second heat exchange medium, wherein the distribution channels (22) each comprise an initial portion (22A) and an end portion (22B).

5. The heat exchanger (7) according to claim 4, characterized in that In order to form the throttling member, an initial portion (22A) and / or an end portion (22B) of the distribution channel (22) further away from the rotation axis (2) and an initial portion (22A) and / or an end portion (22B) of the distribution channel (22) closer to the rotation axis (2) comprise different flow cross sections.

6. The heat exchanger (7) according to any one of claims 1 to 3, characterized in that A turbulator (33) is arranged in the second heat exchange channel (12) to form the throttling member, wherein the turbulator (33) farther from the rotation axis (2) and the turbulator (33) closer to the rotation axis (2) cause different pressure losses.

7. The heat exchanger (7) according to claim 6, characterized in that The turbulator (33) is a spiral turbulator.

8. The heat exchanger (7) according to claim 7, characterized in that The spiral turbulator (33) further away from the rotation axis (2) and the spiral turbulator (33) closer to the rotation axis (2) comprise different spiral lengths.

9. The heat exchanger (7) according to claim 1, characterized in that The heat exchanger (7) is a shell and tube heat exchanger.

10. The heat exchanger (7) according to claim 1, characterized in that The first heat exchange medium is a liquid.

11. The heat exchanger (7) according to claim 1, characterized in that The second heat exchange medium is a gas.

12. The heat exchanger (7) according to claim 11, characterized in that The second heat exchange medium is an inert gas.

13. The heat exchanger (7) according to claim 1, characterized in that The distribution element (17) expands in a conical shape along the flow direction of the second heat exchange medium.

14. The heat exchanger (7) according to claim 1, characterized in that The merging element (18) tapers substantially in a conical shape along the flow direction of the second heat exchange medium.

15. The heat exchanger (7) according to claim 2, characterized in that The throttle orifice (31) is upstream of the inlet opening (29) or downstream of the outlet opening (28).

16. A rotor (1), comprising: Axis of rotation (2), A heat exchanger (7) according to any one of claims 1 to 7.

17. The rotor (1) according to claim 16, characterized in that The second heat exchange channel (12) extends substantially parallel to the rotation axis (2).

18. A rotor (1) according to claim 16 or 17, characterised in that include: a compression unit (3) in which the second heat exchange medium is directed away from the rotation axis (2) to increase the pressure, An expansion unit (4) in which the second heat exchange medium is directed towards the rotation axis (2) to reduce the pressure.

19. A rotor (1) according to claim 16 or 17, characterised in that include: An internal heat exchanger (5) relative to the rotation axis (2) and an external heat exchanger (6) relative to the rotation axis (2).

20. The rotor (1) according to claim 19, characterized in that The external (6) heat exchanger (5) is designed according to any one of claims 1 to 7, wherein the throttling member is configured to throttle the internal flow of the second heat exchange medium of the rotor passing through the internal heat exchange channel to a greater extent than the external flow of the second heat exchange medium passing through the external heat exchange channel.

21. The rotor (1) according to claim 16, characterized in that The rotor (1) is a rotary heat pump.

22. A method for exchanging heat between a first heat exchange medium and a second heat exchange medium inside a rotor (1) according to any one of claims 16 to 20, comprising the following steps: causing the rotor (1) to rotate about a rotation axis (2); guiding the first heat exchange medium along a first heat exchange channel (15) of the heat exchanger (7); A second heat exchange medium is guided along a second heat exchange channel (12) of the heat exchanger (7) at a different distance from the rotation axis (2) of the rotor (1); wherein heat exchange is performed between the first heat exchange medium and the second heat exchange medium along the first heat exchange channel (15) and the second heat exchange channel (12), The features include: By throttling the inner flow of the second heat exchange medium closer to the rotation axis (2) and the outer flow of the second heat exchange medium farther from the rotation axis (2) to different degrees, the flow passing through the second heat exchange channel (12) is homogenized.

23. The method according to claim 22, characterized in that The first heat exchange medium is a liquid.

24. The method according to claim 22, characterized in that The second heat exchange medium is a gas.

25. The method according to claim 24, characterized in that The second heat exchange medium is an inert gas.

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