DE2430435B2 - HEAT EXCHANGER - Google Patents

Description

The invention relates
schür rtr "eirvr;i> ^r e" n: r

one: W'ärnieuu

ί'- T \ V '. Sch ' ¹ .;

T Λ / 1 Γ

YOU IJO

provided rotor for generating a through the rotor directed flow of a first working fluid for the purpose of a heat exchange between the flowing over the blades of the rotor first working fluid and a second working fluid, which is de :; Rotor is directed, the coaxial to the Roior axis in perpendicular to the rotor axis plane, in certain Spaces arranged along the rotor axis and ίο to which the blades are attached and coaxial to the Rotor are aligned in such a way that parts of the blades extend parallel to the longitudinal axis of the rotor, the ring channels via at least one distribution channel! for the incoming second working fluid and at least one collecting channel for the emerging second working fluid with each other to an inner one Are connected to the duct system, which is or collecting duct is connected to connection devices.

From US-PS 32 53 64 ^ is a heat exchanger of this type known, in which the blades are hollow and from the second working fluid itself are flowed through. This training has the disadvantage that the rotor because of the xomplizienen Construction is expensive to manufacture, since each one of the blades with the respective Rina channels must be connected pressure-tight. Another disadvantage is that because of the relatively thick design of the blades on the There is only a comparatively small amount of space for blades on the circumferential surface of the rotor, since there is space between the blades a certain minimum distance must be maintained. so that the first working fluid can flow through quickly.

Considering the many joints between the blades and the hollow ring channels with the known heat exchanger there is always the risk that one of these connection points will leak and needs to be repaired. It is therefore to be assumed that the known heat exchanger is prone to failure.

The invention is based on the object of providing a heat exchanger of the type mentioned at the beginning that is simple and reliable 4f. and still has a large heat exchange capacity.

According to the invention, this task is solved by that the distributor and collecting ducts are arranged parallel to the rotor axis, with the distributor duct opposite the Sammclkanal, and that the blades are designed as thin heat conducting plates are.

The heat exchanger according to the invention is simple in that the second working fluid from Distribution channel flows through the hollow Ringkanäie to the collecting channel and therefore a smaller one The number of pressure-tight connection points results in aK in the known heat exchanger. This increases not only the operational reliability, it also enables the heat exchanger to be manufactured cheaply.

The heat exchanger according to the invention also has a large W'ärmetauschkapazi- ;; ύ earlier. LJ.i the second working fluid due to the uniform arrangement of the rotor sufficiently through-C; can flow. Since the blades are made thin, many blades can be arranged next to each other λ earth, which facilitates the heat transfer. The V-Baptism!: · No-ü? ;; ctabe, ivncrsciis ⁽ \\ - c \ n- qiu ■

Purchströmung of the rotor through the first working fluid and on the other hand for the good heat transfer; inside the rotor.

In the following, exemplary embodiments of the invention are shown on the basis of a drawing. It zeisi

Fig. 1 is a schematic overall sectional view of a preferred embodiment of the inventive concept Heat exchanger,

FIGS. 2 and 3 partial perspective views of the rotor according to FIG. 1,

4a to 4c are schematic views of an exemplary embodiment for the configuration of the flow control at the outlet,

Fi g. 5 is a perspective view of the rotor according to a further exemplary embodiment of the invention,

Fig. 6 and 7 are schematic representations of the course of the Strotiungs by the heat exchanger according to the invention,

Fig. S, 3 and 10 are diagrams in which the behavior through the heat exchanger according to F i ti. 7 Blowing air from the bends along the curves i «t.

Fig. H and 1 2a perspective partial viewers. the fan shovel.

Fig. I2b is a partial view in which the arrangement of baffle segments on the fan blades is shown

13 is a schematic representation of various Developments of the blower air: m. pile up and

14 is a diagram in which the mine's je; Heat exchanger according to the invention according to F ι n .: amount of heat dissipated for different types of skin is plotted over the rotor speed.

In FIG. 1 is a schematic section of the entire heat exchanger shown according to the invention. The heat exchanger has a pair of housings 1 and 2 (only the housing 2 is shown in FIG. 1. See also FIGS. 6 and 7). Between these housings 1 and 2, a channel 3 is formed for the first working fluid, and on the opposite A suction connection 4 and a pressure connection 5 are located at the ends of the channel.

Inside the channel 3 is arranged in the transverse direction to the channel em rotor 6, at the opposite axial ends of which hollow, cylindrical pump chambers 7 and 8 are provided. Ir, the middle of the outer end walls of these pump chambers 7 and 8, hollow shafts IA and SA are attached, which are mounted in bearings IB and SB.

A stationary tube 10 fastened to a carrier 9 extends coaxially through the hollow shaft 7/1. One end of the stationary pipe 10 engages in the pump chamber 7, and a plurality of distribution channels 10/1 for the entering second fluid are attached to this end and extend radially and perpendicularly to the axis of the stationary pipe 10. Each distribution channel 10/1 has an outlet opening 10 B. which opens into the pump chamber 7 in the radial direction.

A blade 11 is arranged in the pump chamber 7, the one straight or curved qui \ section and the fluid in radial Ricir ..: ng distracts. The shovel 11 is concentric around the distributor channel 10-4 in such a tau ai ^ eordne ·. that from the Austritisöffnuim lft / i λι-ιγ.ηιι, Fluid is directed in a radial direction

435

A mounted on the carrier 9 is mounted coaxially stationary crude 12 in the hollow shaft 8 A. Egg: The end of the stationary pipe 12 engages in the Pum penkammer 8 and carries within this pump chamber 8 a guide body 13 for the exiting fluid, which is arranged in a plane perpendicular to the axis of the stationary pipe 12 (see I '' Fig. 4b).

With the reference numeral 14 seals are be distinguished, which verhin a leak between the hollow shaft 7 / and the stationary tube 10 and between the de hollow shaft 8/1 and the stationary tube 12 :. A V-belt pulley! 5 is attached to the hollow shaft HA. The V-belt pulley 15 wire is driven via a V-belt by means of a Antriebseinrich treatment, so that the rotor 6 with the hollow shafts 7 /! and SA and rotates together with the blade 11.

The rotor 6 has several blades 16 and numerous annular channels 17. The blades 16, each because they are curved inwards in the direction of rotation, they are annular around the axis of the rotor ί arranged around parallel next to each other. The ring canals 17. which are each made hollow unc coaxial to the axis of the rotor 6 in on the axis perpendicular planes are in the axial direction arranged at constant distances from one another These .ί ■ 'pile 16 and ring channels 17 are together connected so that they are a coherent Form construction part of cylindrical shape.

The rotor 6 also has a distribution channel IS! Lr for the incoming fluid: as well as a collecting channel 19 : 'W derivation of the! iuids, and both channels extend: -! extend from the pump chamber 7 to the pump chamber 8 along the same circumferential surface of the rotor 6 and run parallel to the rotor axis, with each ring channel 17 at right angles! ■■ chiieiden. The channels 18 and 19 are arranged symmetrically to the axis of the rotor 6. They are hollow and form a distribution channel 18.-1 for fluid entering Jas or a collector 19A for draining off the fluid.

The distribution channel 18 A is on the side de; Pump chamber 8 located at the end closed and open! with the other end into the pump chamber: 7. while the collector 19A is closed at the end located at the pump chamber 7 iiiik! the other end opens into the pump chamber 8. These channels 18 / i and 19/4 are connected to the Rmgkanal 17/1 via the openings Π Β and 17 C, respectively. In the SL way: s; the pump chamber 7 with the pump chamber 8 via the distribution channel 18.Ί, the opening 17ß, the Rmukanal 17.-1. the opening 17C and the collector cap al 19.i connected.

N.iciifülgciKi sol! the flow path of the working fluid through the heat exchanger can be described. The / wide working fluid, which is supplied through the stationary pipe 10 in the direction of arrow A , flows through the V'eueilerkanai IQA and enters the pump chamber 7 at the outlet opening IUB ei; .. In de; Γ, mpei :! aninut 7 becomes the second arivü-iiuiu infoige of the / denlugal force, which over the ■ ii: mi! the? R ■>;<:; 6 rotating blade 11 in the i-iuii .; ungeicitLi ^ ird. printed outwards.

The second anvisiluid takes place under the influence of de; ! •: ir> ·. irkni! :: an Jer! '' umpenk ninier 7 from, strönu

ui; u flows through

24 30 43

penkammer8.

On the other hand, the first working fluid at the sauna connection 4 is _{sucked in by the action of the ScKe Tl 6} and flows into the channel 3, diametrically through the rotor 6 and occurs at the pressure connection? From this, heat is exchanged between the first and second work via the ring channels 17 and the Sch u Mn 16.

The second working fluid, which was passed into the collector chamber ISM, enters the pump chamber 8 em. The pump chamber 8 rotates together with the rotor 6, and the FlSd located on the outer circumference 3es stationary guide body 13 has a higher pressure than the fluid located on the inner circumference of the stationary guide body 13, so that the fluid as a result of this pressure difference from the outer circumference of the stationary Guide body 13 flows through Z center and then exits in the direction of PfeHes B through the stationary pipe 12

The blade 11 is shaped so that the fluid pressure in the rotor 6 is raised without loss. To this For this purpose, the blade 11 can be arcuate or have a curved cross section or, on the other hand, it can be a straight show ^ Act fel In contrast, the guide body 13 is designed so that the fluid uninhibited by the

Leitkorper can pass without a sudden Change of direction and a sudden change in speed Experiments have shown that the design of the guide body 13 has a considerable influence on the pumping action exerts which is caused by the rotation of the rotor 6. In Figures 4a, 4b and 4c

exemplary embodiments are shown for the guide body 13, used in the experiments

? ^e _R i ^ERSU K ^{results showed 'that with a} Ge: measure F ι g. 4 b designed guide body 13 is the largest

Efficiency could be achieved, while the embodiments according to FIGS. 4c and 4a increase ^me . ^nd "" _o ^{ne re} W'Aungsgrade were obtained. This means that the Wu-kung degree decreases as the number of E.ntnttskanäle UA decreases of the guide body 13, the opening of these inlet channels 13 A Begt Tangentialnchtung in the fluid rotation., and they are so designed that they conduct the fluid smoothly to the center of the Ixitkörpers 13, whereby a minimal resistance arises.

P "Sn ^r * i ^{OtOr can be} _k ^aU , ^{Ch SO} constant that the pump chambers are both arranged on one side of the rotor (FIG. 5). In such a company

5r _since ^he ^ ^{r 10 <ί} ί ^Sb | ^{OTHER S0 construction} «^ n ΪΆ tZ λ λ ^^ ¹ , ^Pum P ^eilk ammer 107 exits and via the distribution channel 118 ^, the Rik s.» * The _{course of the flow; of} ^the rotating rotor 6 and the fixed. ^U " ^{d 2 generate} S ^{l becomes} " St by flow ^{m LH pm r e} "t counterclockwise

Sehrich.uS ^ ^ ^ ^{ΛΧΐΜα 16 Are in the} red fid- », η ^inne " f ^krün ™ t. If the

Rank _ne W at ₂ H f ^ " ^so-called " ankine-YVirbel 20 out, the center of which is on the inside

° ^{rS 6 in the} immediate vicinity of the

Sh d \ e F fin
create w _P H ί "I

r k ». ,· of

Sfß.e ^ s _S, Ä? "Ϊ́ ^ f ^ ^{WirbeI stunning"} n * ^Str ° ^{then mt through the} channel 3 and enters

S · ^{A S} ° ^{'che K} ° n ^ Ruktion ^{ta Mnt} i ^and "" ^ r not ^{It is also known> that}

^it is ^the ΤΪ ^{AuSgeStal "esentI} 'ch * affected.

ί I am ^{a warm exchanger}

'Ί · ^{Γ such EIE from} S 8 ^{is l' that} ^ ^{'If d' e throughflow} ömende air ί _2S Fluick with ^niedn g ^en flow resistance arbei- η ^{T-Wa, rmetausc} hleistung in increasing _Mence Ϊ "7? R ^{temperature of the} coming ^{from the} housing NEN _m S of the "WS ^kon _t ^Stant £ ^{n level ha} ^ to kön-" S & SsteH η ^ n? ^{aU Cher} l ^S ° ^{designed to be 'that} moglfcht _ng ^g 7, r ^ ^throughflow quantity of air ER-

Higher - · - ^ ° ^{k is the heat} "

which ^ 7 "Ύ ^{plate 21} equipped, through ufrH c ^increase e of the air flow ] ί is fr > TT ^ei , ⁿ f ^throttle kla _PP e 22. The plate 21 M" ^{aI 3 an} 8 ^eord net and around an axis

»Nschl,« ^ ''"^ ^Ste " ^{e near the Sau} S " Tn Reiz vi ^a " ^geord S ^{et is and a} " ^da ^ housing 1 EL ™" from a position F to a position G

Advertise M ' ^$ ° ■ ·!? ^{therefore the La} S ^{e des Rankine} -

klänne22lf ^V f ^{an rt} c ^W f ^{den kann} · ^{The throttle} aSh.ä ς ^{Ciner position near the D} ™ ck-

ίΐ ^ "^" ⁶ ' ^U " ^{d around an axis 24} point at'enr? ^ · ^8Ι \ the ^{housing 2} adjoining PosLnT, ΐ fj ^{from a} position / in a _forts Z £ ^s . ^ch * ^enk b«. so that the air flow

Can _n S "^ ^" ^{value Nul1 verrin} g ^{ert who}

"Luftstr ^ fn ^eXperi . ^MenteI1 determines that the air flow according to the in Fi e 8 shown

V & D? "? ™ ^{verae" changed} whom? The plate 21 used to increase the air flow

while ^F T ^{position G} g ^ is pivoted, ni ♦ ^d throttle valve22 the position / a Tf ^ ^pressure connection 5 volSS opens ^UCh ^ ^{Γαε ei} " ^a -sz ^ vei SnandS

r ^h ^ ^{Γαε ei} " ^a -sz ^ vei SnandS housing formed by curved pieces 1 and ^{it lo} ß ^a nthmischen spiral e formed structure

D. Fxg. 6 ze _l

schematic end face

. _. , ο serving plate 21 Ü

towards position G iff

684

is panning. In the diagram according to FIG. 9, the curve shows the relationship between the position of the plate 21 and the air flow zxx serving for heat exchange at a point in time at which the throttle valve 22 is fully open and the speed of the rotor is constant. In this diagram, the reference symbols F and G correspond to the positions F and G in FIG. 7. On the other hand, when the throttle valve 22 is moved from position / to position H as shown in FIG. 7 was pivoted, then the air flow decreased according to curves I, II and III according to FIG. 8 from points X, Y and Z to points U, V and W, at which the air flow is zero. It follows that the heat exchanger allows the air flow to be controlled over a wide range.

It is known that the moment of the rotor 6 decreases when a fan of the aforementioned type is operated, when the air flow is decreased by actuation of the throttle valve 22. The advantage of the The mechanism is that the rotor drive force corresponding to that in the diagram of FIG The curves shown decrease when the throttle valve is pivoted increasingly upwards during the to increase the air flow serving plate 21 is brought into a position in which the largest Airflow is enabled.

The heat exchange takes place mainly via the surfaces of the blades 16 of the rotor 6. In general the total area of the blades 16 is very large, and therefore the heat exchanger does not need to be equipped with any additional heat conducting plates when the blades 16 and the different channels made of one material such as B. made of copper, aluminum or brass.

11 and 12 show exemplary embodiments of such blades 16. The blade 16 according to FIG. In Fig. 12a a further embodiment of the blade 16 is shown, which is produced by a wave-shaped bending of a long sheet metal strip to form a V-shaped cross-section, with certain ₈ μ

Parts cut out in the blade plane and derai are bent so that they reach inwards in the direction of rotation of the Ro tor. These guide segments 16 A he stretch along curved lines in the direction of rotation of the rotor 6, as can be seen in Fig. 12b zi. Otherwise, the rotor 6 is self-cleaning, since dust and foreign bodies that collect between the blades 16 on the suction side of the housing from the first working fluid, the perpendicular

ίο flows through the blades to the axis of the rotor 6, conveyed to the pressure side and removed.

In Fig. 14, the test results are plotted in a diagram with four different Heat exchangers were achieved, these heat exchangers exhibiting the following parameters:

Outside diameter of the rotor ... 145 mm

Inner diameter of the rotor 110 mm

Axial length of the rotor 100 mm

Cross section of the distribution channel for the entering fluid and for the Collecting duct of the exiting

Fluids 20 X 20 mm

Number of ring channels 10

Cross-section of the ring channels 4X15 mm

Design of the blades there were two

Types M and N

used (see Fig. 13)

Distance between two adjacent blades 5 and 8 mm

In the diagram of FIG. 14 is the rotor speed Plotted on the abscissa and the amount of heat transferred on the ordinate. The two Four heat exchangers used in experiments had a housing which, according to FIG. 6 from the housings 1 and 2 consisted. Furthermore, 51 water / min at 80 ° C were introduced into the rotor 6, and the inlet temperature of the air, diametrically through the rotor flowed, was 20 ° C.

In addition 7 sheets of drawings

«09534/117

Claims (7)

Patent claims: 1.Heat exchanger with a rotatably mounted rotor provided with blades for generating a flow of a first working fluid directed through the rotor for the purpose of heat exchange between the first working fluid flowing over the blades of the rotor and a second working fluid which is passed through several hollow annular channels of the rotor is. which are arranged coaxially to the rotor axis in planes perpendicular to the rotor axis at certain intervals along the rotor axis and to which the blades are attached and are "aligned coaxially to the rotor in such a way that parts of the blades extend parallel to the longitudinal axis of the rotor, the ring channels over at least one Verteiierkanal for the incoming second working fluid and at least one Sammslkanal are connected for the exiting second A.beitsfluid together to form an internal channel system which is connected to connection devices via the distributor or to the collecting channel, characterized in that the manifold and the Collecting channel (18, 19) are arranged parallel to the rotor axis, wherein the distribution channel (18) is opposite to the collecting channel (19), and that the blades (16) are designed as thin heat conducting plates. 2. Heat exchanger according to claim i. characterized in that two pump chambers (7, 8) are provided in the rotor (6), which are connected both to the openings of the distributing channel (18) or the collecting channel (19) and to the connecting channels: (10, 10.Ί. 10ß; 12. 13) are in connection. 3. Heat exchanger according to claim 1 and 2, characterized in that the pump chambers (7, 8) in the longitudinal direction of the rotor (6) on opposite sides Ends of the same are arranged. 4. Heat exchanger according to claim 1 and 2, characterized in that the Pumpcnkammem (107, 108) are arranged in the longitudinal direction of the rotor (106) at the same end thereof. 5. Heat exchanger according to claims 1 to 3, characterized in that in the one pump chamber (7) several Vcrteilerkaniiie (10 A) are provided for the second working fluid, which introduce the second working fluid radially into the pump chamber (7). 6. Heat exchanger according to claims i to 3, characterized in that in the other Pump chamber (8) a guide body (13) is provided for the second working fluid. the that second working fluid discharges radially from the pump chamber (8). 7. Heat exchanger according to claims 1 to 3, characterized in that in the one pump chamber (7) in the flow direction behind the distribution channels (10 A) blades (11) are arranged