EP2245389B1 - Vanne rotative et pompe à chaleur - Google Patents

Vanne rotative et pompe à chaleur Download PDF

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Publication number
EP2245389B1
EP2245389B1 EP08872649.2A EP08872649A EP2245389B1 EP 2245389 B1 EP2245389 B1 EP 2245389B1 EP 08872649 A EP08872649 A EP 08872649A EP 2245389 B1 EP2245389 B1 EP 2245389B1
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EP
European Patent Office
Prior art keywords
fluid
valve according
longitudinal body
rotary valve
rotating valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP08872649.2A
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German (de)
English (en)
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EP2245389A2 (fr
Inventor
Roland Burk
Thomas Haller
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mahle Behr GmbH and Co KG
Original Assignee
Mahle Behr GmbH and Co KG
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Publication of EP2245389A2 publication Critical patent/EP2245389A2/fr
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Publication of EP2245389B1 publication Critical patent/EP2245389B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B17/00—Sorption machines, plants or systems, operating intermittently, e.g. absorption or adsorption type
    • F25B17/08—Sorption machines, plants or systems, operating intermittently, e.g. absorption or adsorption type the absorbent or adsorbent being a solid, e.g. salt

Definitions

  • the invention relates to a rotary valve according to the preamble of claim 1 and a heat pump according to the preamble of claim 13.
  • WO 2007/068481 A1 describes a heat pump from a fixedly interconnected stack of plate-like hollow elements, wherein the hollow elements comprise adsorber-desorber areas and each represents a hollow element a flow channel.
  • the plurality of flow channels are alternately connected in series with one another via pairs of rotary members arranged at the end of the hollow elements, in order to achieve an optimization of the performance of the heat pump for a given size.
  • a rotary valve according to the invention is not only suitable for controlling a plurality of fluid flows of different temperatures for a heat pump, for example for the recovery of heat, but in general for the alternating interconnection of fluid flows, for. B. also for the recovery of ingredients of a solution z. B. in chemical reactors.
  • the switching element is designed as an axial longitudinal body, which is accommodated in a stationary, substantially cylindrical wall, wherein either the feeders or the discharges via radially directed openings of the wall are indicative.
  • the longitudinal body particularly preferably has a number of axially directed, separate channels for the fluid streams corresponding to the plurality of feeders, each channel having a radial opening for connection to one of the openings of the wall.
  • the axial separate channels can, for. B. be made by axially longitudinal bores.
  • the channels can run straight and parallel, so that it is possible to dispense with a spiraling of the channels known from the prior art.
  • annular sealing means are preferably accommodated on radial projections of at least one of the two longitudinal bodies or walls.
  • the sealing means may also be formed integrally with the longitudinal body and / or the wall.
  • the material of the corresponding component can also have sealing effect, for example, with a suitable choice of material pairings of plastics or plastic and metal.
  • a one-piece design of seals on the respective component can also be provided in the sense that the seals are molded from a different material than the component to this.
  • the longitudinal body is formed as a substantially one-piece component.
  • This can be z. B. be an injection molded part made of a plastic, in particular by one or more steps of post-processing, for. B. by attachment of holes for longitudinal channels, is reworked.
  • the longitudinal body may also be formed as a plurality of longitudinal body elements stacked in the axial direction.
  • Such a division into a plurality of longitudinal body elements allows a modular design that is easily adaptable to different numbers of flow channels in terms of a Glelchteileworkss.
  • At least some of the longitudinal body elements are preferably designed as identical parts.
  • the switching member is penetrated in the axial direction by a rotatable shaft, wherein the shaft is formed in a preferred detail design as a tie rod for holding a plurality of axially successively arranged components of the switching element. hereby the switching element can be easily dismantled for purposes of maintenance or replacement of occluding parts.
  • the switching element is rotatably mounted on the end side via a bearing member, wherein in particular the bearing member has a rotary seal for sealing the fluid.
  • a precise guidance of the switching element is thereby made possible while reducing frictional forces, wherein the rotary seal constitutes an additional barrier against fluid leakage, which is particularly useful in health-hazardous or environmentally hazardous fluids.
  • a bearing member may be provided at the opposite end of the switching element.
  • a rotary valve according to the invention is particularly suitable for interconnecting a large number of feeders and discharges, so that in a preferred embodiment there are at least four, in particular at least eight, feeders and discharges. ,
  • a non-inventive solution of a rotary valve is achieved by providing the separate sealing means in the end regions of the partitions and their sealing support a particularly good sealing of the separate channels of the switching element, whereby efficiency and reliability of the rotary valve over the prior art with simple means clearly is improved.
  • the sealing means may in particular have a U-shaped, H-shaped or X-shaped cross section. Other suitable cross sections are conceivable.
  • the sealing means is formed with an elastic sealing lug, which bears against the inner wall.
  • the sealing means is positively inserted into a groove of the partition wall, whereby measures such as gluing or other expensive attachments can be dispensed with.
  • the channels for changing the assignment are generally advantageous alternately with circumferentially offset, radially directed openings of the inner wall of a stationary inner cylinder overlapping, being provided between the inner cylinder and a surrounding outer housing from each other separate, in the axial direction one behind the other arranged annular chamber.
  • the interconnection is achieved by changing overlap radially directed openings.
  • a desired separation of the openings and channels in the course of sweeping can be achieved in particular by a suitable design of the width of the sealant in the circumferential direction.
  • the sealant while a connection of adjacent flow channels can be prevented at any time of the circulation of the rotating switching element, the average opening times for all of the Strömurigskanäle are reduced accordingly.
  • a narrower in the circumferential direction sealing means may be provided, to avoid an unfavorable connection of adjacent flow channels, the rotating switching member is rotated in order to avoid a mixture of the fluid flows sufficiently fast, step-like switching movements.
  • the object of the invention is achieved for an aforementioned heat pump with the characterizing features of claim 13.
  • the combination of a rotary valve according to the invention with a heat pump is particularly advantageous since the optimization of the rotary valve in terms of tightness or size and the properties of the heat pump are improved in terms of size or performance.
  • the object of the invention is also achieved according to the invention for a heat pump mentioned above, by forming the hollow elements as a respective stack of several parallel layers of sub-elements. This ensures a particularly good heat transfer between the fluid flowing around and the thermodynamically active regions of the hollow elements. As a result, the power of the heat pump can be increased for a given space.
  • the first fluid in exchange with the first zone and the second fluid in exchange with the second zone will be different from one another and have no connection in the circuits.
  • it may also be materially identical fluids which, depending on the embodiment, may also have a connection to one another.
  • the hollow elements are designed as adsorber elements which have an adsorption / desorption region for the working medium in the region of the first zone and a condensation / evaporation region for the working medium in the region of the second zone.
  • adsorber elements which have an adsorption / desorption region for the working medium in the region of the first zone and a condensation / evaporation region for the working medium in the region of the second zone.
  • At least one of the flow channels has end-side connecting pieces, wherein the fluids in the region of the connecting pieces is distributed to a plurality of flow paths.
  • one or more flow paths for the fluid can easily be formed by one or more gaps between sub-elements arranged on top of each other.
  • the hollow elements are each formed as separate modules, which in particular are not in thermal contact with each other. In this way, an undesirable exchange of heat energy between adjacent flow paths is reduced. This is particularly important for such adjacent flow paths, which have a high temperature difference to each other due to the current shading.
  • a layer of a thermally insulating, in particular elastic material can be arranged between adjacent hollow elements, for example, this can be a foamed plastic or a fibrous insulating mat.
  • the valve arrangement can be designed as a connection of a number of discrete, in particular electromagnetically actuated, multi-way valves.
  • a number of discrete, in particular electromagnetically actuated, multi-way valves Particularly in the case of heat pumps with a relatively small number of flow paths, such an interconnection of discrete valves may be expedient, with rotary valves according to the invention being advantageous in particular as the number of flow paths increases.
  • the valve assembly comprises at least one, in particular at least two rotary valves according to one of claims 1 to 12,4da by the rotary valves according to the invention, the fluid flows can be switched inexpensively and reliably.
  • At least some of the flow channels of the hollow elements are connected via elastic deformable connecting pieces with the feeders and / or discharges of the rotary valve.
  • the second fluid is air.
  • air for the purpose of conditioning such as heating or cooling can be passed directly over the hollow elements, in particular the second zone.
  • the air flow can be used for heating or cooling, for example, of a building or vehicle.
  • the air can also generally be regarded as a heat-transporting medium without being used as conditioned ambient air, e.g. is used for people or technical facilities.
  • the rotary valve of the second fluid has a switching member with a, a stepped coiled partition wall, wherein in particular a number of stages of the spiraling corresponds to a number of hollow elements.
  • a switching element can be combined with a single-walled enveloping cylinder, without having to provide a relatively complicated to produce continuous spiraling of the partitions.
  • gaseous fluids such as air at high flow rates and at the same time small pressure differences, since measures such as annular chambers of double-walled outer cylinders could be disturbing here.
  • the switching element is formed of a plurality of in particular designed as identical parts, arranged axially one behind the other switching element elements.
  • the second fluid is distributed via a rotary valve with two flow channels over the second zones (B) of the hollow elements.
  • a rotary valve with two flow channels over the second zones (B) of the hollow elements.
  • a further preferred exemplary embodiment of the rotary valve is characterized in that at least one feed of the plurality of feeders in a first heat exchanger assignment, in particular via a first heat exchanger, such as a heater, is connected to an associated discharge.
  • the heat exchanger is preferably a heat source which is arranged outside the rotary valve.
  • At least one further feed of the plurality of feeders is connected in a second heat exchanger assignment, in particular via a second heat exchanger, such as a cooler, with an associated discharge.
  • the second heat exchanger is preferably a heat sink, which is also arranged outside the rotary valve.
  • the remaining feeds of the plurality of feeders are connected in a passage assignment, in particular via a respective passage, with associated discharges.
  • the above-described rotary valve can replace two in-phase controlled rotary valves, as described earlier. As a result, the number of required seals can be significantly reduced. Furthermore, the friction moments occurring during operation of the rotary valve can be reduced.
  • the above-described rotary valve requires less space than the rotary valves described earlier, which in pairs perform the same function as a single previously described rotary valve. The material used to produce such a rotary valve is also reduced. In addition, long internal parallel fluid paths that result in undesirable pressure drops and internal heat transfers can be reduced. Furthermore, a synchronous in-phase drive of several rotary valves, which requires a high control engineering effort, omitted.
  • the rotary valve according to the invention makes it possible in a simple manner to connect associated inlets and outlets stepwise directly with each other or via one of the two heat exchangers. As a result, the manufacturing costs of the rotary valve can be significantly reduced. In addition, a more compact, flatter arrangement of the overall apparatus is made possible.
  • a further preferred embodiment of the rotary valve is characterized in that the switching member comprises a rotary body having a plurality of through channels connecting the remaining feeds in the passage assignment with the associated discharges.
  • the rotary valve described allows in a simple manner the control of a closed fluid circuit through a plurality of thermally active modules either via one of the heat exchangers, in particular a heat source and a heat sink, or via one of the passageways in the manner of a bypass to the heat exchangers.
  • the location of the interposition of the heat exchanger between each two thermally active modules can be gradually shifted by a movement of the rotating body.
  • a further preferred embodiment of the rotary valve is characterized in that the passage channels extend in the axial direction through the rotary body.
  • the passageways preferably extend straight through the body of revolution.
  • a further preferred embodiment of the rotary valve is characterized in that a plurality of, in particular four, annular chambers extend around the rotary body, which are connected in dependence on the position of the rotary body with one of the feeders and / or one of the discharges.
  • the annular chamber are bounded radially inwardly by the rotary body and radially outward by a housing of the rotary valve.
  • the annular chambers are preferably bounded by radial boundary walls which extend radially outwards from the rotary body.
  • a further preferred embodiment of the rotary valve is characterized in that in each case two of the annular chambers are connected in pairs via one of the heat exchangers.
  • the associated fluid channel extends from one of the feeds via one of the annular chambers to one of the heat exchangers. From the heat exchanger runs the fluid channel then via the associated next annular chamber to the associated discharge.
  • a further preferred embodiment of the rotary valve is characterized in that the annular chambers are connected via radial openings and a broken in the axial direction connecting channel in pairs with one of the feeders or one of the discharges.
  • the connection channels are interrupted by connecting an associated feed to one of the heat exchangers with the associated discharge.
  • the through-channels constitute bypasses which allow fluid flow past the heat exchangers, ie directly between a feed and the associated discharge.
  • a further preferred embodiment of the rotary valve is characterized in that the rotary body is designed and stepwise rotatable in a fixed housing, that the supply are successively connected via different passageways or the Ringkammem and one of the heat exchangers with the associated discharges. This makes it possible in a simple manner that are always connected zwel feeds via one of the heat exchanger with the associated discharge. The remaining feeds are connected via the through-channels directly with the associated discharges.
  • a further preferred embodiment of the rotary valve is characterized in that the housing has substantially the shape of a hollow circular cylinder.
  • the jacket of the hollow circular cylinder is preferably interrupted only by connecting channels which connect the Ringkammem with the associated heat exchangers.
  • the feeds and discharges preferably extend through the otherwise closed end walls of the housing.
  • a further preferred embodiment of the rotary valve is characterized in that the rotary body comprises a plurality of longitudinal body elements stacked in the axial direction.
  • the longitudinal body members may for example be stacked on a drive shaft, the extends through the rotary valve.
  • the longitudinal body elements can be materially connected to each other, for example by welding or gluing. But it is also possible to clamp the longitudinal body elements together.
  • a further preferred embodiment of the rotary valve is characterized in that at least some of the longitudinal body elements are designed as identical parts. As a result, the production and / or assembly of the rotary valve is simplified.
  • the sealing means has a U-shaped, H-shaped or X-shaped cross section.
  • the sealing means has an elastic sealing lug which bears against the cylindrical wall.
  • the sealing means is positively inserted in a groove of the partition.
  • the channels for changing the assignment alternately overlap with circumferentially offset, radially directed openings of the inner wall of a stationary inner cylinder, being provided between the inner cylinder and a surrounding outer housing separate from each other, arranged in the axial direction one behind the other Ringkammem.
  • the channels for changing the assignment alternately overlap with circumferentially offset, radially directed openings of the inner wall of a stationary inner cylinder, being provided between the inner cylinder and a surrounding outer housing separate from each other, in the axial direction one behind the other annular chambers.
  • the switching member has a rotary body with a plurality of through channels, which connect the other feeders in the passage assignment with the associated discharges.
  • passage channels extend in the axial direction through the rotary body.
  • annular chambers extend around the rotational body, which are connected in dependence on the position of the rotational body with one of the feeders and / or one of the discharges.
  • annular chambers are connected in pairs via radial openings and an interrupted in the axial direction connecting channel with one of the feeders or one of the discharges.
  • the rotary body is designed and stepwise rotatable in a fixed housing, that the feeds successively through the various passageways or the annular chambers and one of the heat exchangers are connected to the associated drains.
  • the housing has substantially the shape of a hollow circular cylinder.
  • the rotary body comprises a plurality of longitudinal body elements stacked in the axial direction.
  • the hollow elements are designed as adsorber elements, wherein the adsorber elements in the region of the first zone have an adsorption / desorption for the working fluid and in the second zone a condensation / evaporation area for the working fluid.
  • At least one of the flow channels has end-side connecting pieces, wherein the fluid is distributed in the region of the connecting pieces on a plurality of flow paths.
  • one or more flow paths for the fluid is formed by a gap between sub-elements arranged on top of each other.
  • the flow paths are provided with surface-enlarging structures, in particular ribs.
  • the hollow elements are each formed as separate modules, which are in particular not in thermal contact with each other.
  • a layer of a thermally insulating, in particular elastic material is arranged between adjacent hollow elements.
  • valve arrangement is designed as a connection of a number of discrete, in particular electromagnetically actuated, multiway valves.
  • valve arrangement comprises at least one, in particular at least two rotary valves.
  • the second fluid is air.
  • the rotary valve of the second fluid has a switching member with a one-stage coiled partition wall, wherein in particular corresponds to a number of stages of the spiraling a number of hollow elements.
  • the switching element is formed from a plurality of in particular designed as identical parts, arranged axially one behind the other switching element elements.
  • the second fluid is distributed via a rotary valve with two flow channels over the second zones of the hollow elements.
  • a heat pump is shown in which a plurality of presently a total of twelve hollow elements 1 are arranged in the manner of a stack parallel to each other.
  • the stack of hollow elements 1 is connected via tie rods 2 releasably connected to a structural unit.
  • Each of the hollow elements 1 has a first zone A in the form of an adsorption / desorption zone and a second zone B in the form of a vaporization / condensation zone.
  • the first zone A is penetrated for each of the hollow elements 1 by a respective first flow channel 3 of a flowing around, funded via a pump not shown first fluid and the second zone B is penetrated for each of the hollow elements 1 by a second flow channel 4 of a second fluid, the in the present example, but not necessary, is different from the first fluid.
  • Each of the flow channels 3, 4 in this case has end-side connections 3a, 3b which are opposite to one another and each serve as feeds or discharge lines for the fluid flowing through the flow channels 3, 4.
  • the held together by the tie rods 2 stack of hollow elements 1 is disposed in a support frame 5 of the heat pump.
  • a total of four rotary valves are arranged and connected to the stack of hollow elements 1, wherein two substantially identical rotary valves 6 with the inlets and outlets 3a, 3b of the sorption side A are connected.
  • Two of these, in particular with regard to the number of flow channels separated in the valve, are generally deviatingly constructed, but identical to one another, rotary valves 7 are connected to the second zone or evaporation / condensation side B of the hollow elements 1.
  • the rotary valves 6, 7 are all aligned parallel to each other, wherein central rotary shafts 6a, 7a of the rotary valves 6, 7 are connected to a modular drive unit 8, the Fig. 2 is shown schematically.
  • the drive unit 8 comprises an electric motor 8a through which four drive wheels 8c for synchronizing the respective axes 7a, 6a of the rotary valves 6, 7 are moved by means of a toothed belt 8b.
  • all of the rotary valves 6, 7 are driven at the same angular velocity.
  • the rotary valves 6 of the sorption side A of the hollow elements 1 have a feed region 6b, which has twelve separate feeds 6c, so that each of the twelve hollow elements 1 corresponds to a separate channel within the rotary valve 6.
  • the rotary valves 7 of the evaporator side B have a smaller number of only four separate feeders 7c in a feed region 7b, since on this side of the heat pump usually no so highly differentiated separation of the flow channels is necessary as on the sorption side.
  • a plurality of the hollow elements 1 are connected with respect to their second zone B in each case with one of the flow channels in the valves 7 gleichzeltig. Reference is made to the explanations in the prior art WO 2007/068481 A1 directed.
  • the adjacent hollow elements 1, are held spaced from each other, which is achieved in the present case by suitable spacers 9 between the hollow elements.
  • An air gap thus remains between the hollow elements 1, so that they are thermally insulated from one another.
  • z. B be inserted from foamed polymer or fibrous insulation materials.
  • the individual ports 3a, 3b, 4a, 4b of the hollow elements 1 are connected to corresponding ports 6d, 7d of the rotary valves 6, 7, which extend in each case in a row radially extending from the turn of a discharge region of the substantially cylindrically shaped rotary valves.
  • the individual hollow elements 1 are each designed to optimize the heat exchange with the fluid as a stack of sub-elements 10, which are respectively flowed around by the fluid.
  • Each of the sub-elements 10 is formed as a plate-shaped planar element, in which a plurality of adsorber elements 11 are arranged side by side in the flow direction of the fluid and are material-tightly separated from one another via webs 12 which are vertical with respect to the fluid flow direction.
  • the adsorber elements 11 are predominantly in the region of the first Zone A is arranged (see illustration after Fig. 4 ), wherein in the zone B also separated by the webs 12 evaporation / condensation structures are provided. These structures, not shown, z. B.
  • a heat pump according to the invention is also not limited to the adsorption / desorption principle, but any suitable thermodynamically active hollow elements 1 can be provided, for example chemisorptive hollow elements.
  • Each of the sub-elements 10 is formed as a cover plate 10a material-tight closed plate member. These closed elements 10 are connected via small spacers 14a (see Fig. 6 ) spaced apart from each other and kept at a distance from outer end plates 13 of the hollow elements. In each of the hollow elements 1, which are stacked from each present three sub-elements 10, there are thus four planar flow paths 14 for the fluid. These flow paths 14 are further subdivided by the spacers 14a extending continuously in the fluid flow direction.
  • the spacers 14a can also be impressions in the cover plates 10a and / or end plates 13 for further reduction of the components.
  • the flow paths 14 may be provided with surface-enlarging structures, not shown, such as ribs.
  • a filling tube 16 is arranged on each of the opposite end faces of a respective hermetically separated chamber, so that the chambers can be flowed through in their longitudinal direction, ie perpendicular to the flow direction of the fluid, by the working medium.
  • a vacuum can be applied to one side and the working medium can be supplied on the opposite side via the corresponding filling tube.
  • a further development of such a rotary valve according to the invention is shown, which can be combined in a particularly preferred embodiment with the heat pump described above directly and has the advantages, inter alia, in terms of a smaller size, ease of manufacture and better sealing of the separate channels.
  • a rotatably driven switching element 16 is arranged in a single-walled hollow cylinder 17, which has arranged in a straight row equidistant connection openings 17a for connection to the terminals 3a, 3b of the stack of hollow elements 1.
  • the switching element 16 is in Fig. 8 shown separately. It is a designed as a substantially cylindrical longitudinal body member which is rotatable about a central shaft or axis 18.
  • the switching member 16 has in its circumferential direction a number of axial, parallel bores 16a, the number of which is present twelve and entapricht the number of hollow elements or separate, alternately interconnected flow channels.
  • a number of present annular circumferential radial projections 16 b are provided over the length of the molded as a cylindrical longitudinal body switching member 16, a number of present annular circumferential radial projections 16 b are provided.
  • the projections 16b are made in pairs, so that a ring seal, not shown, is positively held between a pair of projections.
  • a total of sealing members for the formation of equidistant annular chambers 16c are formed, which are fluid-tightly separated from each other via the sealing rings.
  • Each of the annular chambers 16c has a bore 16d radially directed with respect to the fluid flow, which opens into exactly one of the axial channels 16a.
  • the radial bores 16d are correspondingly offset in the circumferential direction relative to each other, so that they form a circumferential spiral with the slope 1.
  • each of the front side axially opening Kanalbohningen 16a with exactly one annular chamber 16c is radially connected.
  • Each of the ring callipers 16 c is aligned in a fluid-tight manner with the other ring chambers in a sealed manner with one of the connection openings 17 a to the stack of hollow elements 1.
  • Fig. 7 shows, the end-side axial openings of the channels 16a pass over corresponding axially directed opening bores 19a of a control disk 19, which is applied end-to-end on the rotary valve and is connected in a stationary and sealing manner to the outer cylinder 17.
  • control disk 19 forms a feed region in the sense of the invention and is at the same time a part of the switching range of the rotary valve.
  • a star-shaped sealing member 20 between the control disk 19 and the end face of the switching member 16 is inserted.
  • the star-shaped fingers 20a of the sealing element 20 engage in radial grooves 16a of the end face of the switching element 16.
  • a system of connecting hoses (not shown) is connected to the supply ports 19a of the control disk 19 and on the other side leads according to the basic concept of the heat pump to other openings 19a or also an outer heat exchanger.
  • For connection to external heat exchangers or heat sources is generally on the state of the art WO 2007/068481 A1 directed.
  • Fig. 9 shows one opposite Fig. 8 with respect to the function identical modification of the switching element 16.
  • the switching element 16 is a stack of longitudinal body elements 21 (see Fig. 10 ) and a differently shaped end piece 22 is formed. At least some of the longitudinal body elements 21 are in each case identical in construction and constructed rotated by a fractional angle according to the number of channels to each other.
  • a form-fitting receptacle 23 is provided in the longitudinal body elements 21 for the positive connection with a central drive shaft, wherein the receptacles 23 has a symmetry corresponding to the number of channels.
  • the receptacle 23 has only a sixfold divided rotational symmetry, so that two longitudinal body elements 21, which are different relative to the positioning of the radial opening 16d relative to the receptacle 23, are alternately used to construct the entire stack of twelve longitudinal body elements.
  • shaft and recording have a 12-fold split symmetry, in which case only one type of longitudinal elements is needed.
  • the rotary valves 6, 7 are made of a sufficiently temperature-resistant plastic, wherein the stack of hollow elements 1 is constructed with respect to its walls and connections substantially of metal sheets.
  • plastic for the construction of the rotary valves 6, 7 in particular the use of postcrosslinked thermoplastics is recommended.
  • changing the interconnection of the flow channels is achieved by covering with respect to the fluid flow axially directed openings, whereby the length is considerably reduced and the number and shape of the components are reduced or simplified.
  • FIG. 11 to FIG. 18 show embodiments and modifications of a rotary valve with a switching element 24 with radial partitions.
  • the channels separated by the radially extending partition walls 25 via an inner cylinder with circumferentially offset holes 26 (see Fig. 16 ), so that the channels in the course of the movement of the partition walls 25 each cover with different openings 26 successively.
  • each of the holes 26 terminates in a formed between the stationary inner cylinder 27 and a stationary outer cylinder 28 annular chamber 29.
  • In the outer cylinder 28 are equidistantly arranged in a straight line connections 30 for connection to the stack of hollow elements 1 is provided.
  • the switching operation for changing the interconnection of the flow channels takes place in such an embodiment by the sweeping of the partition walls 25 via the openings 26 which are directed radially relative to the fluid flow.
  • Fig. 11 shows an arrangement of the switching element 24 of such a rotary valve together with a feed region 31, which is similar in design to the switching element 16 from Fig. 8 is formed here, but does not take over the function of a switching element, since in the feed no change in the assignments of the flow channels takes place.
  • the feed area 31 and the switching element 24 are connected to each other as non-rotatably connected, separate components via a shaft 18 passing through them in common in the manner of a tie rod by means of a locking screw 32.
  • the star-shaped radially extending partitions 25 have advantageously in their radial end regions resiliently arranged sealing means 33 in the manner of axially extending sealing strips.
  • Fig. 13 shows an exemplary embodiment in which the sealing strips 33 have a U-shaped cross-section, wherein an additional resilient element 34 between the end face of the partition wall 25 and the sealing means 33 is inserted. As a result, a particularly good sealing of the individual axial channels is achieved against each other.
  • FIG. 14 A modification of such a sealing strip at the radial end portions of the partition walls 25 is in Fig. 14 shown.
  • the seal 33 is formed in the manner of a stroking over the inner wall sealing lip, which is inserted via a kederartige thickening 35 in a corresponding end-side groove of the partition wall 25 positively.
  • FIG. 12 Another advantageous development is in Fig. 12 shown, in which the central shaft 18 of the switching member 24 is mounted on at least one end of the rotary valve in a bearing bush 36, which also has a rotary seal 37.
  • the rotary seal 37 additionally seals any leaks of fluid relative to the outer space.
  • FIGS. 17 and 18 Another embodiment of a rotary valve according to the invention is in the FIGS. 17 and 18 shown. Also in this valve, the interconnection of the flow paths by means of radially directed partitions 25 and radially directed openings in the wall of an inner cylinder 27, which open into annular chambers of an outer cylinder, not shown, takes place.
  • each of the axially longitudinal, separated from the partitions 25 chambers of the switching member is connected via a respective bore 38, each having a different concentric annular groove 39, wherein each of the annular grooves 39 is in a plane with the other annular grooves 39, however has a different diameter.
  • FIGS. 17 and 18 only two annular grooves 39 are shown to corresponding changing circuit of only two flow paths.
  • connection of the annular grooves 39 of the switching element with external feeds of the fluid flows via holes 40 in a fixedly connected to the cylinder feed plate 41.
  • Each of the holes 40 opens into exactly one of the annular grooves 39, so that according to the representation 17, each of the openings 40 of Feeding plate 41 is connected independently of the rotational position of the switching member with exactly one of the axial partitions 25 formed axial chambers of the switching member.
  • O-ring seals 42 between the feed plate 41 and the walls of the annular grooves 39 are respectively provided.
  • FIGS. 17 and 18 is not shown for reasons of clarity of the outer cylinder with its inner cylinder 27 surrounding annular chambers.
  • Fig. 19 schematically shows the switching function of a rotary valve with seven alternately switched flow paths or fluid flows. There are three switch position A, B, C shown, wherein the position C is transferred to the position A after a further step. On the input side there is the numbering of the fluid streams 1-7 and on the output side the numbering of the hollow elements 1-7. After seven changes of the assignment or a full rotation of the rotary valve, the original interconnection is reached again.
  • non-inventive embodiment of a rotary valve 7 for combination with a heat pump has only two chambers or flow channels 44, 45 and is particularly suitable to be combined with air as a second fluid to exchange heat with the second zones B of the hollow elements 1.
  • the rotary valve 7 of this embodiment has an only single-walled outer cylinder 47, which has arranged in a straight row radial openings 48 for connection to the hollow elements 1.
  • a rotatable switching member 24 accommodated in the cylinder 47 comprises a hub or shaft 46 from which radially two partition walls 25 extend to the cylinder wall.
  • the partitions 25 neither straight in the axial direction, as from the state of the art WO 2007/068481 A1 known, running continuously coiled. Instead, the partitions 25 are coiled in stages, as can be seen in particular from the unrolled illustration Fig. 22 results.
  • the stepwise winding of the partitions 25 of the switching member 24 allows a simple structure of a plurality of axially successively arranged switching member parts 49, 50th Fig. 23 shows a switching member part 49, as it is provided in the central region as a repetition of identical parts, which are each offset by a certain number of degrees to each other.
  • the switching member parts 49 have plane, parallel to the axis of rotation radially extending partition wall portions 49a and perpendicular to the rotation axis extending to the Trenwandsegmente 49a subsequent Abdecksektoren 49b of 30 ° in this example opening angle, by means of which the stepped coiled chambers or flow channels 44, 45 of the Switching member 24 are formed.
  • the terminal arranged, forming end pieces switching member parts 50 have a single Abdecksektor 50 b with an opening angle of 180 °, said 180 ° -Abdecksektoren at the opposite ends of the switching member 24 are arranged inversely to each other.
  • an external supply and an external discharge to the chambers 44, 45 are formed in a simple manner, since the fluid (in the present case air) can be supplied only at the one end side of the outer cylinder 47 and removed at the opposite end face (see also the developed representation to Fig. 22 ).
  • the supplied air can be referred to as evaporator air or as condensation air.
  • Another preferred, for the basic principle but not necessary detail of the rotary valve consists in a radial end of the partition wall sections 25, 49 provided, the curvature of the cylinder 47 following Abdeckfahne 51.
  • the opening angle of the Abdeckfahne 51 is about as large as the opening angle of the openings 48th the cylinder wall, so that in a position (see illustration in Fig. 21 ) are each individual or with appropriate design, more of the hollow elements 1 with respect to the second zone B are closed. This represents an adiabatic intermediate step of the interconnections of the flow paths in operation, whereby the effectiveness of the heat pump can be further improved.
  • Fig. 25 is the switching task of a rotary valve 100 according to another embodiment shown as a 2-D scheme.
  • the rotary valve 100 comprises a plurality of feeders 101 to 112 and discharges 201 to 212, which can be individually assigned to the feeders 101 to 112 via connecting lines 126 or 128 and 129.
  • the additions and removals are z. B. connected to thermally active modules 301 to 312.
  • the rotary valve 100 comprises a switching member 114, which in turn comprises a rotary body 115, which, as indicated by an arrow 116, is rotatable.
  • a first heat exchanger in the form of a cooler 118 is shown, to which a pump 119 is connected downstream.
  • a second heat exchanger is designed as a heater 120.
  • This in Fig. 25 illustrated rotary valve 100 serves to flow through twelve thermally active modules, as described in advance with reference to the embodiments of Fig. 1 to 24 are described to control with a heat transfer fluid.
  • the twelve thermally active modules 301 to 312 are serially flowed through by a heat transfer fluid.
  • the heat source in particular the heater 120
  • the heat sink in particular the recooler 118
  • the rotary valve 100 has the task to gradually move the location of the interposition of the heater 120 and the recooler 118, without having to be co-rotated, as would be required in direct implementation of the schematic circuit. Deviating from the presentation of Fig. 25 Therefore, the radiator 118, the pump 119 and the heater 120 are fixedly disposed outside of the rotary valve 100 in the following figures of an exemplary structural implementation.
  • the rotary valve 100 is off Fig. 25 initially shown in a schematic process.
  • the rotary valve 100 comprises twelve feeders 101 to 112, which are also referred to as inputs and are combined to form a feed region 81.
  • the rotary valve 100 comprises twelve discharges 201 to 212, which are also referred to as outputs and are combined to form a discharge region 82.
  • the feeders 101 to 112 can be connected in a different manner to the drains 201 to 212 by means of the switching member 114, which comprises the rotary body 115, when the rotary body 115 rotates in the direction of the arrow 116.
  • the radiator 118 and the heater 120 are disposed outside of a housing 125.
  • Each supply 101 to 112 and each discharge 201 to 212 is associated with an opening in an end face of the housing 125, which has substantially the shape of a hollow circular cylinder.
  • the feeds and discharges open into the end faces of the housing 125.
  • Each opening in the housing 125 is an opening in the rotary body 115 can be assigned.
  • each of the feeders 101 to 112 can be connected to the associated discharge 201 to 212 in a defined manner.
  • the feeders 102 to 106 and 108 to 112 via a respective passage 126 with the associated discharges 202 to 206 and 208 to 212 are connected.
  • the passageways 126 extend straight through the rotary body 115 therethrough.
  • the feeders 101 and 107 are connected via interrupted connecting channels 128, 129 respectively to the associated discharge 201, 207.
  • the connecting channels 128, 129 are subdivided by means of dividing walls or the like into subchannels 128a, 128b or 129a, 129b such that they force a flow diversion via the radiator 118 or the heater 120.
  • four annular chambers 131 to 134 are within the housing 125, which in the settlement of the Fig. 26 and 27 when straight channels are shown.
  • the supply 101 is connected via the interrupted connecting channel 129 with the annular chamber 133, which in turn is connected to the heater 120.
  • the heater 120 is connected via the annular chamber 134 with the discharge 201.
  • the feed 107 is connected via the annular chamber 131 to the radiator 118, which in turn is connected via the annular chamber 132 and the interrupted connecting channel 128 with the guide 207.
  • the through channels 126 and the broken connection channels 128, 129 are assigned to other feeders and discharges. This displacement preferably takes place stepwise such that the rotary body 115 always comes to a halt when the openings of the channels 126, 128, 129 provided in the rotary body 115 overlap with the corresponding openings in the housing 125.
  • Fig. 27 the rotation body 114 is rotated by one step compared to the representation of Fig. 26 shown.
  • the supply 102 is connected via the heater 120 to the associated discharge 202.
  • the feed 108 is connected via the cooler 118 with the associated discharge 208.
  • the remaining feeds 101, 103 to 107, 109 to 112 are connected via the through-channels 126 directly to the associated outlets 201, 203 to 207, 209 to 212.
  • Fig. 28 to 30 is that in the Fig. 26 and 27 simplified illustrated rotary valve 100 shown in somewhat more detail.
  • the rotary body 115 In the cylindrical housing 125, which is cut longitudinally, the rotary body 115 is rotatably driven by means of a mounted drive shaft 150 sealed to the environment.
  • two ceramic sealing plates 151, 152 are provided on each end face of the housing 125.
  • the ceramic sealing plate 151 is fixedly assigned to the housing 125.
  • the ceramic sealing plate 152 is associated with the rotary body 115 and rotates with this relative to the ceramic sealing plate 151 and the housing 125.
  • the two plate pairs can be resiliently biased against each other via a (not shown) spring means.
  • annular chambers or annular spaces 131 to 134 are in each case via a radial opening 141 to 144 with the associated connecting channel 128, 129 in connection.
  • the radial openings 141 to 144 constitute a radial aperture window providing fluid communication between the annular chambers 131-134 and the radially inwardly disposed axial communication passages 128, 129 which, unlike all other communication passages 126, pass through at least one partition 128c and 129c, respectively are divided into two subchannels 128a and 128b and 129a and 129b.
  • the association between the sub-channels 128a, 128b and 129a, 129b and the annular chambers 131 to 134 are preferably selected so that each two adjacent annular chambers 131, 132 and 133, 134 with corresponding, so aligned with each other feeds 101; 107 and discharges 201; 207 are connected. Thereby, depending on the position or rotation of the rotary body 115, always a fluid path through the heater 120 and another of the total of twelve existing fluid paths through the cooler or recooler 118 out.
  • Fig. 28 The fluid passes from the supply 101 via the radial opening 143 and the annular chamber 133 to the heater 120, as indicated by an arrow 121.
  • a further arrow 122 is indicated that the fluid passes from the heater 120 via the annular chamber 134 and the radial opening 144 to the discharge 201.
  • the fluid passes from the supply 107 via the radial opening 141 and the annular chamber 131 in the radiator 118, as indicated by an arrow 123.
  • a further arrow 124 is indicated that the fluid passes from the radiator 118 via the annular chamber 132 and the radial opening 142 to the discharge 207.
  • Fig. 28 it can be seen that the rotor axis is mounted with the bearings 155, 156 in the cylindrical housing and the entire inner volume is sealed by a sealing element 154 from the environment.
  • a sealing element 154 apart from the two preferably ceramic surface seal pairs 151, 152 only three further sealing elements 157, 158, 159 required to seal the four annular chambers 131 to 134 in the axial direction against each other.
  • FIGS. 29 and 30 are two cuts through the rotary valve 100 off Fig. 28 shown.
  • Fig. 29 is indicated by arrows 161 and 162, as the fluid passes from the heater 120 to the radial opening 144.
  • Fig. 30 is indicated by further arrows 163, 164, as the fluid passes from the radiator 118 to the radial opening 142.
  • the sections show the rotational body 115 subdivided into 12 axial chambers, which is preferably stacked on a common shaft 150 with positive locking from plastic injection-molded elements.
  • the reference numerals 128 and 129 denote the passageways which are divided by partitions 128c and 129c into two sub-channels 128a, 128b and 129a, 129b, respectively.
  • the rotary body 115 has only interrupted passage channels in the manner of the reference numerals 128 and 129, which are each subdivided again by partition walls 128c and 129c into subchannels 128a, 128b or 129a, 129b and have radial aperture windows to the annular spaces 131 to 134, which in turn are paired with two heat exchangers, referred to as "heatsinks" and "recoolers".
  • heatsinks two heat exchangers
  • the Fig. 32 shows the rotary valve in the following position.
  • This modified embodiment allows a dependent of the switching position of the rotary valve assignment thermally active modules 301 to 312 to at least two separate driven with their own funding fluid circuits within which the associated modules are flowed through in parallel.
  • the two embodiments according to Fig. 26 . 27 and 31, 32 are only two examples of the division of the passageways according to the categories 126, 128 and 129. Further designs of the through-channels to these categories are of course possible and also useful for particular applications.
  • the rotary valve 100 has, among other things, the following advantages: High integration of switching functions replaces two conventional rotary valves; reduced effort for drive and control; compact, material-saving construction; simple, cost-effective manufacturability, for example of plastic injection-molded parts; easy to implement, low-wear surface seal over. Ceramic discs or ceramic plates 151, 152; short flow paths with low heat exchange between the individual flow paths; low friction and required drive torque; low bypass losses.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Multiple-Way Valves (AREA)

Claims (13)

  1. Vanne de rotation comprenant
    un espace d'arrivées (6b, 19 ; 81) comprenant une pluralité d'arrivées séparées et fixes (6c, 19a ; 101 - 112) pour plusieurs flux d'un fluide, et
    un espace d'évacuations (82) comportant en particulier une même pluralité d'évacuations séparées et fixes (6d, 17a ; 201 - 211) pour les flux du fluide,
    où il est prévu, entre l'espace d'arrivées (6b, 19 ; 81) et l'espace d'évacuations (82), un espace de commutation ayant un bloc de commutation (16, 31, 24 ; 114) tournant autour d'un axe,
    où, dans une première position du bloc de commutation (16 ; 114), la pluralité des arrivées (6c, 19a ; 101 - 112) est reliée, dans une première correspondance, à la pluralité des évacuations (6d, 17a ; 201 - 212), et
    où, dans une deuxième position du bloc de commutation (16 ; 114), la pluralité des arrivées (6c, 19a ; 101 - 112) est reliée, dans une deuxième correspondance, à la pluralité des évacuations (6d, 17a ; 201 - 212),
    caractérisée
    en ce que le bloc de commutation (16 ; 114) comprend une pluralité d'ouvertures (16a, 126, 128, 129) déplacées en même temps que le bloc de commutation et traversées axialement, dans la direction de l'axe de rotation, par les flux de fluide, ouvertures qui, au cours de la rotation du bloc de commutation (16 ; 114), recouvrent de façon alternée une pluralité d'ouvertures (19a, 101 à 112, 201 à 212) fixes et orientées axialement,
    où les différentes correspondances des arrivées (19a ; 101 - 112), par rapport aux évacuations (17a ; 201 - 212), se produisent sous l'effet des recouvrements alternés des ouvertures (16a, 19a) orientées axialement.
  2. Vanne de rotation selon la revendication 1, caractérisée en ce que le bloc de commutation (16) est configuré comme un corps longitudinal axial qui est logé dans une paroi (17) fixe, sensiblement cylindrique, où soit les arrivées (19a), soit les évacuations (17a) sont reliées par des ouvertures de la paroi (17) orientées radialement.
  3. Vanne de rotation selon la revendication 2, caractérisée en ce que le corps longitudinal présente un nombre de canaux (16a) correspondant à la pluralité d'arrivées (19a), lesdits canaux prévus pour les flux de fluide étant séparés et orientés axialement, où chaque canal présente une ouverture radiale (16d) servant à la communication avec l'une des ouvertures (17a) de la paroi.
  4. Vanne de rotation selon l'une des revendications 2 ou 3, caractérisée en ce qu'au moins l'un des deux composants, à savoir le corps longitudinal (16) ou la paroi (17), présente des éléments d'étanchéité circulaires (16b), de forme annulaire, qui coopèrent à chaque fois de façon étanche avec l'autre des deux composants, à savoir le corps longitudinal (16) ou la paroi (17), de sorte que les ouvertures (17a) de la paroi sont séparées les unes des autres.
  5. Vanne de rotation selon la revendication 4, caractérisée en ce que les éléments d'étanchéité comprennent des moyens d'étanchéité qui sont logés sur des parties saillantes radiales (16b) d'au moins l'un des deux composants, à savoir le corps longitudinal (16) ou la paroi (17).
  6. Vanne de rotation selon la revendication 4, caractérisée en ce que les éléments d'étanchéité (16b) sont configurés en formant une seule et même pièce avec le corps longitudinal et / ou avec la paroi.
  7. Vanne de rotation selon l'une quelconque des revendications 2 à 6, caractérisée en ce que le corps longitudinal (16) est formé comme un composant pratiquement d'un seul tenant.
  8. Vanne de rotation selon l'une quelconque des revendications 2 à 6, caractérisée en ce que le corps longitudinal (16) comprend une pluralité d'éléments de corps longitudinal (21) empilés dans une direction axiale.
  9. Vanne de rotation selon la revendication 8, caractérisée en ce qu'au moins quelques-uns des éléments de corps longitudinal (21) sont configurés comme des pièces identiques.
  10. Vanne de rotation selon l'une quelconque des revendications précédentes, caractérisée en ce que le bloc de commutation est traversé, dans une direction axiale, par un arbre tournant (18), où en particulier l'arbre (18) est configuré comme un tirant d'ancrage servant au maintien de plusieurs composants (16, 21, 24, 31) du bloc de commutation, lesdits composants étant disposés axialement les uns derrière les autres.
  11. Vanne de rotation selon l'une quelconque des revendications précédentes, caractérisée en ce que le bloc de commutation est logé en rotation, côté extrémité, via un élément de palier, où en particulier l'élément de palier présente un joint de rotation servant à assurer l'étanchéité par rapport au fluide.
  12. Vanne de rotation selon l'une quelconque des revendications précédentes, caractérisée en ce que les arrivées et les évacuations sont au moins au nombre de quatre, en particulier au moins au nombre de huit.
  13. Pompe à chaleur comprenant
    une pluralité d'éléments creux (1), où dans chacun des éléments creux (1) se trouvent au moins une première zone (A) et une deuxième zone (B) servant au déplacement d'un moyen de travail disposé dans l'élément creux (1), en fonction de grandeurs relatives à l'état thermodynamique,
    où chacun des éléments creux (1) est relié thermiquement à sa première zone (A) par un premier canal d'écoulement (3) de l'élément creux (1), traversé par un premier fluide, et est relié à sa deuxième zone (B) par un deuxième canal d'écoulement (4) de l'élément creux (1), traversé par un deuxième fluide, de sorte que de l'énergie thermique peut à chaque fois être échangée entre l'un des fluides et l'une des zones (A, B), et
    un agencement de vannes (6, 7), où les canaux d'écoulement de l'une des zones peuvent être interconnectés entre eux séquentiellement, grâce à l'agencement des vannes (6, 7), et un ordre de succession de l'interconnexion se modifie au cours d'un fonctionnement de la pompe à chaleur, au moyen de l'agencement des vannes (6, 7),
    caractérisée
    en ce que l'agencement des vannes (6, 7) comprend une vanne de rotation selon l'une quelconque des revendications précédentes.
EP08872649.2A 2008-02-22 2008-12-08 Vanne rotative et pompe à chaleur Not-in-force EP2245389B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102008010662 2008-02-22
DE102008053555 2008-10-28
PCT/EP2008/010383 WO2009103325A2 (fr) 2008-02-22 2008-12-08 Vanne rotative et pompe à chaleur

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Publication Number Publication Date
EP2245389A2 EP2245389A2 (fr) 2010-11-03
EP2245389B1 true EP2245389B1 (fr) 2016-10-12

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US (1) US8621883B2 (fr)
EP (1) EP2245389B1 (fr)
CN (1) CN101965489B (fr)
DE (1) DE102008060698A1 (fr)
WO (1) WO2009103325A2 (fr)

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DE102009036544A1 (de) * 2009-08-07 2011-02-10 Behr Gmbh & Co. Kg Rotationsventil und Wärmepumpe
JP5849359B2 (ja) 2009-11-06 2016-01-27 マーレ インターナツィオナール ゲーエムベーハー 吸着原理に従うヒートポンプ
DE102011003664A1 (de) * 2011-02-04 2012-08-09 Behr Gmbh & Co. Kg Wärmepumpe
DE102014211703A1 (de) 2013-06-24 2014-12-24 MAHLE Behr GmbH & Co. KG Rotationsventil für eine Adsorptionswärmepumpe
JP6403449B2 (ja) * 2013-07-01 2018-10-10 キヤノン株式会社 シート処理装置及び画像形成装置
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Also Published As

Publication number Publication date
EP2245389A2 (fr) 2010-11-03
CN101965489A (zh) 2011-02-02
WO2009103325A2 (fr) 2009-08-27
CN101965489B (zh) 2014-01-01
WO2009103325A3 (fr) 2009-10-15
DE102008060698A1 (de) 2009-08-27
US8621883B2 (en) 2014-01-07
US20110030408A1 (en) 2011-02-10

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