DE1453616A1 - Diaphragm pump - Google Patents

Description

Augsburg, October 29, 1962

Kobertshaw-Fulton Controls Company, I70I, Byrd Avenue, Eichmond (Virginia), United States of America

Diaphragm pump

The invention relates to an improved type of diaphragm pump, the drive of which is driven by an electromagnetic pump Vibrator takes place. Such membrane pumps can be used, for example, as fluid pumps or also as vacuum pumps Find application.

The diaphragm pump according to the invention is particularly suitable as a vacuum pump for lint er pressure control systems for Control of the program flow of program-controlled devices, whose] action organs respond to negative pressure.

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According to the invention, such a diaphragm pump has a housing half provided with an inlet chamber, furthermore one, Housing half provided with an outlet chamber and an annular disk-shaped, flexible membrane, the inner edge of which is attached to one of the two housing halves and the outer edge of the other housing half, so that between the two Housing halves a pump chamber is formed in which a pumping effect is achieved in that the one housing half is moved axially back and forth relative to the other housing half by means of an electromagnetic vibrator.

The diaphragm pump according to the invention thus has a number of novel features, which in the course of the following Description are set out in detail.

The invention is now described in detail below For example, described with reference to the accompanying drawings with reference to some preferred embodiments. In the Drawings represent:

Fig. 1 is a side view of a, through a

electromagnetic vibrator, driven diaphragm pump according to the invention in one of the numerous positions in which such a pump can be operated, whereby the pump shown can be used, for example, as a vacuum pump,

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Fig. 2 is an end view of the diaphragm pump shown in Figure 1 seen in the direction of arrows 2 * -2,

Pig. 3 shows a bottom view of the diaphragm pump shown in Figure Λ , seen in the direction of arrows 3-3,

4 shows a view in the manner shown in Figure 1 diaphragm pump overall in the direction of arrows 4-4 -. - see

Fig. 5 is a section along the plane 5-5 in Figure 1-, seen in the direction of the arrow,

FIG. 6 shows a central longitudinal section through the in FIG. 1 Diaphragm pump shown on an enlarged scale,

Figure 7 is a view of an inlet or outlet valve body the diaphragm pump shown in Figure 1,

8 shows a partial section from the sectional view of the B.gur 6 on an even larger scale, which Shows details of the arrangement of an exhaust valve,

Pig. 9 shows a partial section from the sectional illustration of Figure 6 on the same scale as Figure 8, showing details of the inlet valve assembly shows,

10 is a circuit diagram of the electrical excitation circuit for the drive vibrator of the diaphragm pump,

11 is a line diagram showing the application of the vibrator-operated diaphragm pump according to the invention as part of an underpressure program control system shows,

Fig. 12 is a partial view of part of the in

Figure 11 schematically shown control system,

13 shows a partial longitudinal section through part of a another embodiment of an outlet chamber of a diaphragm pump according to Figure 6,

Fig. 14 is a schematic side view of another Embodiment of a diaphragm pump arrangement according to the invention,

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Pig. 15 a partial central longitudinal section through the in

Figure 14 shown diaphragm pump arrangement according to the invention, on a larger scale,

16 shows a central longitudinal section through the pump arrangement according to FIGS. 14 and 15 flexible membrane used,

"Fig. I? a partial central longitudinal section through a further embodiment of a diaphragm pump arrangement according to the invention and W

18 shows a central longitudinal section through which is used in the pump arrangement according to FIG coming flexible membrane.

The diaphragm pump illustrated in Figures 1 to 13 of the drawings 20 according to the invention has an electromagnetic drive vibrator 22, which is combined by means of a corresponding "connection element 24 with the pump to a common A vibrator pump unit 23rd This vibrator pump unit according to the invention is improved in many respects over known arrangements of this type

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Drive element, provided one of such drive motors essentially linear oscillatory motion of required Strength and amplitude can be tapped.

The drive vibrator according to the invention has a Vibrator coil 26 and a TJ-shaped iron lamellar core with pole pieces 30 and 32. The drive vibrator and the diaphragm pump according to the invention can by a common, simple connecting part 34- are held together, which for example, can be arranged below or to the side of the vibrator or the pump. The drive vibrator is involved together with a vibrator armature 36 made of metal, which can have a rectangular shape, for example, and im Can be relatively thin compared to its area, as can be seen from Figures 3 and 5 of the drawings is. This vibrator armature is supported by a leaf spring 38 held, which in turn held between corresponding spring clamping jaws 40 and 42 on the connecting part 34 will.

The mass and mass distribution of the vibrator armature, the spring characteristics and the length of the leaf spring 38 can be chosen so that between the drive pulses of the Drive vibrator 22, which can be operated, for example, at a frequency of 60 Hz, and these mechanical ^ parts There is a response.

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The vibrator anchor 36 has rectangular slots 44, whose cross-section is slightly larger than the cross-section of xler pole shoes 30 and 32 of the vibrator core, so that these with Game can protrude through the slots. This makes it possible to move the vibrator armature 36 with respect to the pole pieces and 32 of the vibrator core with practically any amplitude within the maximum permissible stroke of the Su operating diaphragm pump to swing back and forth without disturbing influences between the armature and the core. A.

The anchor slots 44 also permit operation of the Vibrators without the necessary mutual adjustment of the vibrator armature and the vibrator core in view of changes in the pump load, fluctuations in the operating voltage or other external influences, which normally lead to a decrease in the pump output at a certain nominal operating voltage.

The drive vibrator can, for example, be operated with _t single-phase Λ alternating current with 60 periods. As the circuit diagram shown in FIG. 10 of the drawings shows, the operating current can be taken from a normal power line with an operating voltage of 115 V and an operating frequency of 60 periods and from the coil 26 of the vibrator core 28 via a rectifier 48 arranged in one of the two supply lines

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are fed. With appropriate redesign dee Vibrator armature and the armature spring can be the drive vibrator can also be operated without the interposition of a rectifier 48 with 120 periods, although the vibrator is connected to a normal single-phase AC power source of 115 V * with 60 periods can be connected.

However, if the diaphragm pump according to the invention with 60 Periods is operated, then with otherwise the same spring width and thickness, the spring length can be greater than when the diaphragm pump is operated with 120 periods. This makes it possible to use the same power supply Vibrator coil to make the pump stroke larger. A lower operating frequency the diaphragm pump thus increases the service life of the same.

The diaphragm pump itself can be attached to a pump bracket 50 be attached, which in turn on the connecting element 34 is attached. You pump holder 50 can be elastic and is by means of fastening screws 52 simultaneously with the Vibrator spring retaining jaws 40 and 42 on the connector 34 attached.

If the pump holder 50 is designed to be elastic, then character whose mechanical resonance frequency be equal to the pulse frequency of the drive vibrator 22, that is to say approximately the value of

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60 Hz, which in turn increases the pump stroke and thus the pump efficiency is improved at the same time.

The pump holder is, however, preferably made rigid in order to avoid undesired bending of the holder, which may lead to the vibrator armature swinging beyond the ends of the pole pieces of the vibrator core and then gets caught outside of the vibrator core.

The diaphragm pump 20 is within a longitudinal slot 54 ν held in the pump holder 50, through which, as in ~ 6 of the drawings, the pump inlet connection 56 is also passed through * on this pump inlet connection 56, a washer 53 can be pushed on, after which A cutter 60 is screwed onto the thread of the inlet connection can be, so that the washer 58 and the pump housing half 62 are firmly clamped on the pump holder 50 are.

The diaphragm pump 20 is connected to the vibrator armature 36 via a similar, threaded connecting rod 64 which in turn is connected to the vibrator armature by means of a connecting element 66, which may consist of neoprene or any other elastic material.

The connecting element 66 can, for example, be placed around the connecting rod 64 in the form of a sleeve and *

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within a part 70 offset on both sides The bore 68 of the vibrator armature 36 is at rest. By means of clamping nuts and 74- the connecting element 66 may refer to FIG Vibrator η nker 36 are clamped accordingly.

By means of a counter nut 76, the connecting rod on the housing half 78 containing an outlet chamber Membrane pump 20 be attached, which has an end threaded hole has into which the end of the connecting rod 64 is screwed.

Through this mutual connection between the vibrator motor 22 and the diaphragm pump 20 are at the same time mutual axial distance set.

The connecting element 66 is a large part of the Record circular arc-shaped oscillating movement of the vibrator armature, so that the connecting rod 64 is an im substantial linear reciprocating motion transmits to the pump housing half 78, whereby the pump efficiency is substantially increased .. The hardness of the connecting element 66 and the degree to which it is in operation of the pump each is compressed, as well as the strength with which the clamping nuts 72 and 74- are tightened, are selected in such a way that that there is a most favorable efficiency for the overall arrangement. The rule of thumb is that the lower the

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Hardness of the connector 66 and the lower the force is, hit which the clamping nuts 72 and 74- are tightened, within the practically occurring operating ranges of the arrangement, the pump efficiency will be all the higher.

The outlet valve arrangement 86 of the diaphragm pump 20 can be seen in FIGS. 6 and 8 of the drawings. The pump housing half 62 has a circular shoulder 94, in which a circular writing 92

ti can occur, which together with an outlet valve housing 96, ^ which is arranged on the other side of the pump membrane 82, holds this'. The circular disk 92, the pump diaphragm 82 and the outlet valve housing 96 are held together by means of a sleeve 98 which has a collar 100 on the one hand and a collar 102 on the other hand, the latter also representing the outlet valve seat. The outlet valve arrangement 86 held together in this way by this sleeve 98 is screwed as a whole into the pump housing half 78 containing the exhaust chamber. _t ä

The outlet valve housing 96 has, as can be seen from Figure 8 of the drawings, an annular groove 106 which passes through lateral groove flanks 108 and 110 is limited in such a way that the groove width is somewhat larger than the thickness of one in FIG of the drawings is an exhaust valve body shown in elevation. The outlet valve seat 102 is, as shown in Figure 8 of the drawing

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can be seen, something about the plane 109 of the groove wall 110 in front, so that the end face on the left in the drawing 112 of the valve body 84 rests on the left side flank 108 of the hanging groove 106 with slight pressure. This lies at the same time the right end face of the exhaust valve body in the drawing 84 with light pressure on the front edge of the valve seat 102, so that the outlet valve ait kept closed with light pressure.

The inner groove edges 116 and 118 can be sharp-edged. In the exhaust valve housing 96, the annular groove is on the right in the drawing 106 a circular shoulder 122 is formed which receives the valve seat 102. The inside edge 120 of this paragraph can have a radius of curvature of 0.1 ma.

By this circular shoulder 122, the valve noise is reduced because the valve body thereby only the very small valve seat edge area 114 touches. In addition, the paragraph 122 allows the through the sleeve 98 and over the Valve seat 102 air entering this annular space to expand there before it passes through the passage openings 123 the valve disc 84 exits, whereby the air velocity of the exiting air is reduced. That way will avoids the valve noise, which otherwise occurs with air pumps, in which the valves only through the internal Air pressures are kept in their seats.

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That shown in Figures 6 and 9 of the drawings Inlet valve assembly 80 is with the. Exhaust valve arrangement 84-identical. The inlet valve body 80 is also in an annular groove 106A within that containing the inlet valve chamber Pumpöngehäusehalfte 62 held, this annular groove 106A in turn has Kutflanken 108A, 110A, whose in the drawing left HutiLanke with the face 112A of the turn disc-shaped valve body 80 cooperates. The one in the Drawing on the right end face of the valve disk 80 acts in turn with the edge 114A of a valve seat 102A formed in the valve housing half 62. As shown in Figure 9 of the As can be seen in the drawings, all parts of the intake valve assembly are included 80 substantially identical to the exhaust valve assembly 96 shown in Figure 8 of the drawings, where the only thing to note is that while the outer edge 124 * the front air outlet opening of the outlet valve housing 96 can be sharp-edged, the outer edge 124A of the air outlet opening of the inlet valve shown in FIG must be slightly rounded, the radius of the rounding being about 0.5 mm. The passage openings 81 of the Inlet valve disk 80 can be identical to the passage openings 123 of the outlet valve disk 84-.

The shape and dimensions of the pump housing half are chosen in such a way that, in view of the type of pump selected and the pump stroke characteristics, a good volumetric Efficiency results.

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This results, for example, from the fact that in the Pump housing half 62 of the above-mentioned circular shoulder 94 is provided, in which during the holding disk 92 for the pump membrane during pump operation can slide in.

It is characteristic of the operation of the diaphragm pump 20 that the pump, based on that in ligur 6 of the drawings the center position of the pump diaphragm 82 shown, executes an essentially simple harmonic oscillating movement, as supplied by the drive vibrator 22. The one about the connecting rod 64 transmitted drive force first moves the membrane 82 and the associated pump parts from the Pump housing half 62 away to the left. This becomes the within the pressure prevailing in the suction chamber 125 of the pump is reduced. As a result, the outlet valve disk 84 rests against theirs in a sealing manner Valve seat 102 on, while the inlet valve disk 80 after is moved to the left of its associated valve seat 102A and thus the air located in the pump inlet pipe 56 allows entry into the pump 20. The pump stroke speed decreases to the extent to which the pump stroke limit is achieved so that the pressure change occurring in the pump suction chamber 125 is reduced to the same extent until the pump stroke speed reaches the value JJuIl at the end of the left movement of the pump diaphragm, which leads to The consequence is that the pressure drop at the inlet valve 80 is also the

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Value reaches zero and this inlet valve is closed as a result. Due to the now in the leaf spring 38 stored energy now begins a movement of the pump membrane to the right, so that the pressure in the pump chamber 125 now rises and the outlet valve 84- opens. As a result, the air is now expelled from the pump chamber through the sleeve 98 into the outlet chamber 88, whereby a slight back pressure is generated, the In connection with the arrangement of the pump chamber 88, a damping effect with regard to the air outlet noise exerts · The air reaching the outlet chamber 88 then passes through the outlet port 90 into a Air outlet line 91> the length of which is again selected so that that there is a further attenuation with regard to the air outlet noise. In the air outlet line 91 For example, a foam rubber plug 93 may be arranged, the one causes further noise reduction.

If the diaphragm pump 20 is only to be used as a vacuum pump, according to a modified version, shown in FIG ■; · Drawings illustrated embodiment of the invention j Outlet chamber 88A made of a porous material, for example % '■ be formed from metal powder? 8A sintered together, see above

; that their chamber wall density is just so great that

... an air outlet through the outlet chamber wall gives the desired damping effect. The shape of the outlet chamber 88A can be the same as in FIG. 13 of the drawings

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Figure 6 of the drawings, the shape of the outlet chamber shown may be selected. The outlet nozzle 9O _4, the discharge line and the Schaumgummipfropfen 93 can of course be omitted in this case, since the air so filtered according as it emerges already in the penetration of the Austrittskammerwandung 7SA and outlet noise is attenuated according to terms.

Small air pumps, 'if not quite careful are constructed, generally subject to very large noises. With regard to the noise attenuation achieved the air pump according to the invention is a uniquely cheap one Construction. As can be seen from Figure 7 of the drawings is, the two valve disks 80 and 84 each have a circular disk shape. The high noise-dampening effect in the construction of these valves is based on the fact that these two Valve disks are held and arranged in their retaining grooves 106 and 106A in the particular manner described above.

According to this particular construction, the two lie Valve disks 80 and 84 only on very narrow annular areas of the valve seats 102 and 102A, which, as described above and can be seen from the drawings, slightly above the retaining groove flanks 110 and 110A protrude to the left. In addition, the valve groove areas in question are circular Paragraphs 122 and 122A are provided, the purpose and operation of which has also already been described above.

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This protrusion of the two valve seats 102 and 102A to the left causes the two valve disks 84 and 80 to have a barely perceptible curvature, which in turn only exerts a very low closing force on the valve seats 102 and 102A, through which the respective contact surfaces or 114 and 112A or 114A are only exposed to a very low surface pressure. As a result, the two valves always automatically return to their closed positions as soon as the air speed and the air pressure at these valves approach the m value ITuIl at the end of the pump stroke. In this way it is achieved that almost no valve noise occurs.

The remote areas 122 and 122A near the Valve disk retaining grooves 106 and 106A also reduce valve noise as they help the two Valve disks each rest only on the mentioned very small annular areas of the valve seats 102 and 102A. Except-' These two recessed areas 122 and 122A represent expansion spaces through which the noise of the " Valve disk openings 81 or 12 $ escaping air is reduced. This also makes the pump noise significant which normally occurs in pumps whose valves are only caused by those occurring inside the pump Differences in pressure are kept on their seats.

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Another advantage of having a drive vibrator 22 driven diaphragm pump 20 according to the invention is the uniformity of dynamic operational behavior achieved between these two elements. This is done according to the invention achieved in that the end faces 150 and 152 of the pole pieces of the drive vibrator 22 are beveled. As can be seen from Figure 3 of the drawings, the end faces of both pole shoes 30 and 32 are beveled. These beveled end faces of the pole pieces of the lamellar core act in a manner to be described below with a corresponding effect conically shaped part 154 of the interior of the pump housing half 62 together. The cone angle of the conical extending part 154 of the pump housing half 62 can be 15 ° this, as can be seen from Figure 6 of the drawings is, with reference to the mean vertical position of the membrane 82 measured angle exceeded or fallen below can be. If the air flow inside the pump is only slight during pump operation or if there is no air flow at all, so there is between the outlet chamber 88 and the suction chamber the pump has a maximum pressure difference and the elastic and flexible membrane 82 is consequently to the right in Pressed towards the pump housing half 62 towards whose conical inner surface 154 it can lay on. Through this causes -.

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1) the effective cross section of the pump diaphragm 82 with increasing pressure difference in

is reduced to the same extent,

2) the center of vibration of both the diaphragm as well as the vibrator armature 56 to the right, i.e. from the pole shoe end faces I50 resp. is moved away and

3) the now changed operating position of the Vibrator armature result in an expansion of the air gap ^ between armature and vibrator coil core has, the size of this respective air gap is determined by the slope of the pole piece end faces 150 and 152 and is thus determined results in a reduction in the magnetic attraction force.

The interaction of these three factors results in a completely new method for limiting the maximum pressure difference with maximum air flow and no loss of performance, if | for example with a significantly lower pressure difference . a significant amount of air must be suddenly withdrawn from a vacuum program control system or the like. In addition, the size of the maximum pressure difference can be adjusted to the desired extent over a wide control range can be changed by the vibrator armature by means of the two Tension nuts 72 and T ^ with reference to the vibrator core

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is adjusted speaking and also the connecting rod is adjusted by means of the lock nut 76 by Depending on If desired according to a desired smaller or larger average pump capacity, the air gap accordingly is set smaller or larger. '-

If a larger amount of air suddenly has to be withdrawn from the vacuum control system in question, does the lower pressure difference thus applied to the pump automatically allow the diaphragm 82 to use a larger effective surface _? because at that moment the. The membrane immediately begins to work at a greater distance from the hollow conical surface 154 of the pump housing half 62 * In addition, the center of vibration of the overall arrangement moves further to the left, so that now the air gap between the vibrator armature 36 and the vibrator coil core 28 narrows again, which is the pole that the electromagnetic force of attraction of the coil core 28 increases again and the pump stroke is increased again as a result.

The relationship between the hollow conical surface 154 of The pump housing half 62 and the membrane 82 thus each result an automatic reduction of the pump stroke as soon as the respectively desired negative pressure or the respectively desired one The pressure difference is achieved in that part of the pump diaphragm 82 rests against the hollow conical surface 154. Intended to

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{However, suddenly a larger amount of air is withdrawn from the system, when the negative pressure prevailing in the system has already partially decreased, then the membrane 82 continues to work from the hollow cone surface 154, so that now a larger effective membrane area is effective and also at the same time results in a larger diaphragm stroke, so that now the volumetric performance of the diaphragm pump 20 increases.
*. . .

Figures 11 and 12 of the drawings show a lower M-pressure irogrammsystem 159 "which may for example be operated with the previously described diaphragm pump arrangement according to the invention ■■■". On the smooth surface 164 of a slide block or the reading head 162 is a Erogrammkarte or a program movie 160 passed away.

The so-called reading head 162 has one or more passage channels 166 which are provided with openings 186 in the Open out sliding surface 164 of the read head. The passage channels 166 are made of elastic, for example made of plastic existing hoses 167 with one or more vacuum motors or actuating elements 170 connected, which in turn, levers, switches or the like of a machine, for example a washing machine, can operate.

The read head 162 also has one or more inlet ports 172 with openings 174 in the read head

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.; · * ■; ■ / V ^: · "■■■■■ .-. ■

Open onto sliding surface 164. The channels 172 can, for example Open into a common suction line 176, which in turn is formed by an elastic, for example made of plastic existing hose 177 to the inlet port 156 of the Diaphragm pump 23 is connected, which was described in detail above with reference to Figures 1 to 10 and 13 of the drawings has been described.

The program card or program film 160 have a number of bulges or connecting channels 176 through which two or more outlet openings 168 and 164 can each be connected to one another, as shown in FIGS Figures 1T and 12 of the drawings can be seen. The hands these bulges 176 each lie sealingly on the sliding surface 164 of the reading head and the bulges in question each constitute a vacuum-tight connecting bridge between the relevant actuator I70 and the Vacuum source 23 represents.

These bulges 176 are in no way I78 or 180 arranged and are each close enough to one another so that in each case between the openings 168 and 174 one im substantially uniform connection is made when these bulges are above the openings in question. In this way it is possible to narrow the distance between these bulges of a relevant row of bulges

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make than the diameter of the openings to be connected to one another by these bulges.

Is an actuator that responds to negative pressure

170 have been excited by the fact that a membrane arranged therein

171 is exposed to the negative pressure of the control system, so can a de-excitation of the relevant element can be achieved in that the negative pressure prevailing in the relevant channel 166 is interrupted, so that the relevant membrane 17I either under the action of atmospheric pressure or is moved back into its original position by spring action or by both actions. The negative pressure prevailing in the relevant channel can be interrupted, for example, by leading a through hole 182 arranged in the film 160 over the relevant opening 168 of the sliding surface of the lee head. In this way, the atmospheric air can enter the channel 166 in question and allow the membrane 171 in question to return to its original position. Ä

Normally, the suction openings 1-4 opposite the openings 182 are not uncovered by the film 160, so that, as a result of the application of the film 160, this is avoided becomes that the vacuum breaks down in the relevant channel or in the collecting channel 176 and thus always a negative pressure on the pump 20 is maintained.

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Because of the relatively small dimensions of the vacuum chambers the actuating elements 170 and the connecting channels 166 are each only a small volume of air, the inlets 182 into the vacuum control system let in. For this reason, the diaphragm pump 20 works normally over relatively long periods of time under negative pressure without a noticeable amount of air being conveyed will. You ability of the pump diaphragm 82, its effective

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Membrane surface due to contact with the hollow conical surface 154 · the Reducing pump housing half 62, as a result, allows the pump 20 to always work with the lowest possible energy consumption.

Referring to Figure 14 of the drawings now a further embodiment of a diaphragm pump according to of the invention described generally with the reference numeral

190 and by an electromagnetic vibrator

191 is driven. The diaphragm pump itself is labeled with the reference number 192 designated.

As can be seen from FIG. 14, an essentially C-shaped holding frame 193 opposing legs 194 and 195 which essentially approach one another are directed.

Above the frame leg 194 of the frame 193 is a electrical excitation coil 196, so that the frame leg

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at the same time forms the core of the coil 196.

At the end of the leg 195 of the frame 193 is a leaf spring 197 attached, which tries to hold a vibrator armature 198 in a position in which it is shown in FIG Drawings is shown so that he is excited when the Coil 196 comes into coverage with the coil core 194. Of the Vibrator armature 198 can therefore swing backwards or away from it in the direction of the web 199 of the C-shaped frame 193.

The diaphragm pump is located on this web 199 of the frame 193 192 attached, which in a manner to be described below is connected to the vibrator armature 198 that it, as soon as the armature performs its oscillating movement, in itself is operated in a known manner.

The diaphragm pump 192 can be used, for example, in a vacuum control system of the type described above Maintain negative pressure.

As can be seen from Figure 15 of the drawings, has the diaphragm pump 192 according to the invention, an inlet chamber containing pump housing half 200, further a, a discharge chamber containing pump housing half 201 and also a flexible membrane 202, the inner edge 203 in a manner to be described below gas-tight with the,

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the outlet chamber containing the pump housing half 201 connected and the outer edge 204 of which via an outwardly protruding flange 205 containing the inlet chamber Pump housing "half 200 is turned up so that between the with the two housing halves 200 and 201 cooperating membrane 202 and the housing half 200 a pump chamber 206 is formed.

The membrane 202 is kept under tension between the two pump housing halves 200 and 201 of the membrane pump 192, this membrane tension in a manner to be described below in all working positions of the pump membrane 202 is retained.

The pump housing half 200 containing an inlet chamber, has a substantially frustoconical part 20? on, which merges into an outer flange 205 on the side of the larger diameter. This outer flange 205 has an im essentially triangular, outwardly tapering cross-section.

Inside the frustoconical part 207 of that Pump housing half 200 containing inlet chamber is a Paragraph 208 arranged, which is attached to a hollow truncated cone Inner wall 209 connects, which in turn also in the ' Outer flange 205 runs out.

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. The frustoconical part 207 of FIG. 11, the inlet chamber containing pump housing half 200 merges on the side of the smaller diameter into a housing connector 210, which is penetrated by a hole 211.

The pump housing connector 210 of the pump housing half is passed through a bore 212 in the frame 193 and a flat contact surface 213 of this pump housing half lies flat against this path. On an external thread of the pump housing socket 210 a retaining nut 214 is screwed on, which this pump housing half and thus the entire diaphragm pump holds firmly to the frame 193.

Inside the pump housing half 200 containing the inlet chamber is a valve seat 215 'on the left end face. formed, which cooperates with an inlet valve body 216, which in turn in an annular groove 21? is held. Of the Inlet valve body 216 is in turn provided with one or more passage openings 218, each outside of the Valve seat 215 lie. ·

So will the. Valve body 216 in the suction stroke of the diaphragm pump * as a result of a corresponding deflection of the pump diaphragm 202 also bulged to the right, so the medium to be demanded by the pump can be fed through the bore 211 of the Pump housing connector 210 get into pump chamber 206,

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while when the valve body 216 move back to the left and in the manner shown in Figure 15 of the drawings can apply to its valve seat 215, the pumped medium is prevented from escaping from the pump chamber to get back to the bore 211 so that it is the extension stroke the diaphragm pump 192 comes.

You, a discharge chamber containing the pump housing half has a central bore 219 which the pump chamber 206 the diaphragm pump 192 connects to a cavity 220 which is arranged further to the right in the housing half 201.

At the mouth of the bore 219 in the housing cavity an annular valve seat 221 is arranged, which cooperates with an outlet valve body 222, which in turn is accommodated in a hanging groove 223 of the housing half 201. The valve body 222 has one or more passage openings 227, which in turn are outside the annular Valve seat 221 lie. ,

If the outlet valve body 222 is pressed to the left on its valve seat 221 during the suction stroke of the pump 192, so arises in the pump chamber 206 for the suction stroke and negative pressure necessary to open the valve 216, during the Valve body 222 bulges to the right in the pressure stroke of the pump and thus allows the medium conveyed by the pump,

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from the pump chamber 206 through the openings 224 through, into a pump room. 220 to flow.

An axial flange 225 protrudes from the rear face of the pump housing half 201 on the right in the drawing be pushed over spoke-like arms 226 of a separate housing connector 227 and then bent inward can be, whereby the housing connector 227 fixed to the housing half 201 is held.

A porous Sing 228, for example made of foam plastic, is over the pump housing connector 227 pushed and wira held on it by a retaining plate 229, which by means of a central threaded hole on a Thread 230 of a connecting rod 231 is screwed on. The other side of the foam plastic ring 228 rests against it the hand of the axial flange 225 of the pump housing half 201. The medium conveyed by the diaphragm pump is therefore after Leaving the pump chamber 206 and passing the outlet valve 222 through the pores of the foam plastic ring 228 ejected into the outside atmosphere.

The housing connector 227 is by means of a central internal thread 230 onto the external thread of the connecting rod 231 screwed on, which in turn is fastened to the vibrator armature 198 by means of an elastic connecting element 232

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is. The vibrator armature 198 can thus in turn be essentially one Describe a circular path, while the connecting rod 231, the pump housing half 201 within swings back and forth in a substantially straight path.

As can be seen from Figures 15 and 16 of the drawings is, the outer edge 204 of the flexible membrane 202 is pulled inward at 2J3, creating an inner annular groove 234 is formed.

The inner edge 203 of the flexible membrane 202 is thickened towards the inside and is located in an annular groove 235 of the Housing half 201 containing the outlet chamber, which is located between the actual housing body and one inside the housing arranged outer flange 236 is formed.

The flexible membrane 202 is provided with annular regions 237 238 provided with a smaller wall thickness, each of which lies between the membrane edges 204 and 203. Through these ring areas reduced wall thickness, the bending and tensile stresses on the membrane 202 during operation of the pump localized, whereby the wear of the membrane is reduced.

It will now be described how the in Figure 15 of the Diaphragm pump 192 shown in the drawings is assembled.

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The inner edge 2035 of the flexible membrane 202 is either in front of the pump housing nozzle 227 and the porous king 228 on the pump housing half containing the outlet chamber have been attached in the manner described above or after this has happened, turned into the annular groove 235 of the housing half 201, the outer flange 256 still the shown in dashed lines in Figure 15 of the drawings Assumes position which a slight slipping of the inner edge 203 of the membrane 202 over this splash ensures.

As soon as the inner edge 203 of the membrane 202 rests properly in the annular groove 235 of the housing half 201, the outer flange becomes 236 bent towards the housing body, as shown in Figure 15 is shown in full lines. In this way, the inner edge 203 of the membrane 202 is solid and gas-tight connected to the housing half 201 *

Then the housing half containing an inlet chamber 200 applied to the housing half 201 containing a discharge chamber and the outer edge 204 of the flexible one Membrane 202 is over the peripheral flange 205 of the housing half 200 slipped over, as shown in Figure 15 of the drawings. The flexible membrane 202 is now between the two housing halves 200 and 201 under tension, as a result of which these two housing halves are connected to one another on the same side

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are coupled that between the membrane 202 and the pump housing half 200 the pump chamber 206 is formed.

The fully assembled diaphragm pump 192 becomes then attached to the web of the frame 193 in the manner described above, and then the vibrator anchor 198 is attached to the connecting rod 231 screwed on.

The mode of operation of the diaphragm pump 192 corresponds to essentially that of the diaphragm pump 20 described above, with the exception that the areas 237 and 238 are reduced Wall thickness of the flexible membrane 202 the bending and tensile stresses on the membrane locally during pump operation Restrict, so that the wear of the membrane 202 is reduced is.

Referring now to Figure 17 of the drawings, a further embodiment of a diaphragm pump according to the invention will now be described, indicated generally by the reference numeral 239. Those parts of the diaphragm pump which are identical or similar to corresponding parts of the diaphragm pump 192 just described above are denoted by the same reference numerals with the addition of the index ^M a ^w .

The diaphragm pump 239 acts essentially like that Diaphragm pump 192 and has one containing an inlet chamber Pump housing half 200a, furthermore one, an outlet chamber

009816 / CU69

holding pump housing half 201a and a flexible diaphragm 202a as can be seen from FIGS. 17 and 18.

The pump housing half 201a containing an outlet chamber is essentially identical to the previously described pump housing half 201 and that containing an inlet chamber Pump housing half 200a is essentially identical to the pump housing half 200 described above, with the exception of that the circumferential flange 205a of the pump housing half 200a has a rectangular cross-section, ™

The pump diaphragm 202a of the diaphragm pump 239 is essentially identical to the previously described flexible pump diaphragm 202, with the exception that the outer edge 204a of the Membrane also has a substantially rectangular cross-section Has. On the inside, this membrane edge 204a has a cross-section which is also essentially rectangular Hingnut 254a equipped, by means of which he over the circumferential flange 205a of the housing half 200a in the in Figure 17 of the drawings slipped over the manner shown can be.

Otherwise, the inner edge 203a of the flexible pump diaphragm 202a can be attached to the pump housing half in the same way 201a, as previously described in connection with the pump diaphragm 202. The assembly of the The pump takes place in such a way that finally the external

00 9 816/0469

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edge 204a of the pump membrane 202a over the peripheral flange 205a the pump housing half 200a is slipped over, whereby in turn the membrane 202a between these two housing halves 200a and 201a is held in tension.

As can be seen from Figure 17 of the drawings, the end wall 240 is that containing the inlet chamber Pump housing half'200a on the one hand and the outer edge 204a der.Pumpenmembran 202a on the other hand designed so that the The flexible pump diaphragm does not move during the delivery stroke can put on the front side of the pump housing half 200a. As a result, the wear of the pump diaphragm 202a becomes significant degraded.

While the pump housing half 201a containing an outlet chamber relative to that containing an inlet chamber If the pump housing half 200a swings back and forth, the outer edge 204a of the pump diaphragm 202a acts with the peripheral flange 2Ö5a of the pump housing half 200a together so that one "Shoe waxing" is avoided, i.e. that an oscillating movement of the membrane 202a with simultaneous contact the end wall of the pump housing half 200a is excluded. The special rectangular cross-sectional shape of the peripheral flange 205a of the pump housing half 200a prevents the outer edge 204a of the pump diaphragm 202a from during the The activity of the diaphragm pump 239 to oscillate back and forth.

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That shown in Figures 17 and 18 of the drawings Has embodiment of a diaphragm pump according to the invention consequently, except those features that match the features the membrane pump 192 described above are identical or similar, and a number of them are also novel and useful features.

009816/0469

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Claims (24)

Ί4536Τ6 claims 1.J diaphragm pump, characterized by an annular disk-shaped Pump diaphragm (82 or 202 or 202a), the outer edge of which (204 or 204a) on one pump housing half (62 or or 200a) and their inner edge (203 or 203a) on the other pump housing half (78 or 201 or 201a), the inner wall of one pump housing half being in the shape of a hollow truncated cone (154 or 209 or 209a) is designed that the pump diaphragm can apply to them in a lift position. 2. Diaphragm pump according to claim 1, characterized in that the pump diaphragm (82 or 202 or, 202a) in each stroke, position is tense. _ 3 · Diaphragm pump according to claim 1 or 2, characterized in that that the inner edge of the pump diaphragm (203 or 203a) through plastic deformation of the material (with 236 or with 236a) on the relevant pump housing half. (201 or 201a) is attached (Figures 14 to 18). 4. Diaphragm pump according to one of claims 1 to 3, characterized characterized in that the pump membrane (202 or 202a) 009816/04 6 9 - 36 - H53616 is narrowed in cross section in the vicinity of one of its clamping edges (203 or 204 or 203a or 204a) (at 237 or at 238 or at 23? a or at 238a), so that the elastic ¹ deformations of the membrane concentrate essentially on this area (Figures 14 to 18). 5. Diaphragm pump according to claim 4, characterized in that cross-sectionally narrowed areas (237 or 238 or 237a or 238a) near both JSinspsnnr boundaries (203 and 204 ' or 203a and 204a) of the pump membrane (202 or 202a) are provided (FIGS. 14 to 18). 6. Diaphragm pump according to one of claims 1 to 5 »thereby characterized in that the outer edge of the pump diaphragm (204 or 204a) is slipped over elastically on one half of the pump housing (200 or 200a) is attached (Figures 14 to 18). 7 · Diaphragm pump according to claim 6, characterized in that that the pump membrane outer edge (204 or 204a) over an outwardly protruding flange (205 or 205a) of one pump housing half (200 or 200a) is slipped over (Figures 14 to 18). 8. Diaphragm pump according to claim 7, characterized in that the cross section of the outwardly projecting pump housing flange (205 is triangular and extends outwards 009816/0469 - 57 - tapered (Figures 14 to 16),: 9 · Membrane pump according to claim 7, characterized in that that the cross section of the outwardly protruding pump housing flange (205a) is rectangular (Figures 17 and 18). . 10. Diaphragm pump according to claim 9, characterized in that the cross section of the outer edge (204a) of the pump diaphragm (202a) is also rectangular (Figures 17 and 18). 11. Diaphragm pump according to claim 10, characterized in that the end face of one pump housing half (200a) between the hollow-conical inner wall (209a) and the peripheral flange (205a) protrudes in a ring-like manner (240) and that the membrane outer edge (204a) is designed in such a way that the membrane inner surface (257a) is located at a certain distance from this housing ring surface (FIGS. 17 and 18), 12. Diaphragm pump according to one of claims 1 to 11, characterized in that the pump diaphragm (82 or 202a) to the extent of the in the pump chamber (125 or 208 or 208a) prevailing negative pressure on the hollow frustoconical inner wall (154 or 209 or 209a) of one pump housing half (62 or 200 or 200a) (Figures 1 to 18). 13. Diaphragm pump according to one of claims 1 to 12, characterized in that at least one of the two pump 00 98 16/04 6.9 - 38 - U53616 housing halves (62 or 68 or 200 or 200a or 201 or 201a) has a valve seat (102 or 102A or 215 or 221 or 215a or 221a), with each of which a valve body (84 or 80 or 216 or 222 or 216a or 222a) interacts, each in a hanging groove (106 or 106A or 217 or 223 or 217a or 223a) of the relevant valve housing half is held (Figures 1 to 18). 14. Diaphragm pump according to claim 13, characterized in that the valve body in question (84 or 80 or 216 or 222 or 216a or 222a) for the purpose of reducing the valve noise due to its inherent elasticity in elastic contact on the valve seat concerned (102 or 102A or 215 or 221 or 215a or 221a) (Figures 1 to 18). 15. Diaphragm pump according to one of claims 1 to 14, characterized in that a pump housing half (62 or 200 or 200a) an inlet chamber (125 or 208 or 208a) and that the other housing half (78 or 201 or 201a) one on the other side of the pump diaphragm (82 or 202 or 202a) located outlet chamber (88 or 220 or 220a) (Figures 1 to 18). 16. Membrane pump according to claim 15 «characterized in that that the outlet chamber (88 or 220 or 220a) is at least partially covered by a porous body (78A or 228 or 228a) 009816/0469 ^ ,: - 39 - bordered or filled in (Figures 1 to 18). 17 diaphragm pump according to one of claims 1 to 16, characterized in that one of the two pump housing halves (78 or 201 or 201a) is provided with a magnet armature (36 or 198 or 198a) is connected (Figures 1 to 18). 18. Diaphragm pump according to claim 17 «characterized in that the magnet armature (36 or 198 or 198a) can be moved along an arcuate path, while the pump housing half connected to - ^ m (78 or 201 or 201a) along a straight path is movable (Figures 1 to 18). 19. Membrane pump according to claim 17 or 18, characterized in that that the connection between the relevant housing half (78 or 201 or 201a) and the magnet armature (36 or or 198a) by an elastic intermediate member (66 or 232 or 232a) is produced (Figures 1 to 18). 20. Diaphragm pump according to one of claims 17 to 19, characterized characterized in that the magnet armature (36 or 198 or 198a) by means of an electromagnetic vibrator (26, 30 or 194, 196) is actuated (Figures 1 to 18). 21. Diaphragm pump according to claim 20, characterized in that the electromagnetic vibrator (26, 30 or 194, 196), the magnet armature (36 or 198 or 198a) and the diaphragm pump (20 or 192 or 239) itself on a common frame 009816/0 46 9 H53616 (34, 50 and 193) are arranged (Figures 1 to 18). 22. Diaphragm pump according to claim 20 or 21, characterized in that the electromagnetic vibrator (26, 30 or 194-, 196) a U-shaped coil core (30 or 193) has, on one leg (30 or 194) of which the magnet coil (26 or 196) is arranged (Figures 1 to 18). * 23. Diaphragm pump according to claim 22, characterized in that the pole shoes (30, 32) of the. Vibrator magnet core ä bevelled at the end (at 38) (Figures 1 to 13). 24. Diaphragm pump according to one of claims 1 to 23, characterized in that the with the inlet chamber (125 or 208 or 208a) equipped pump housing half (62 or 200 or 200a) is fixed, while the one provided with the outlet chamber (88 or 220 or 220a) Pump housing half (78 or 201 or 201a) can oscillate relative to this first-mentioned pump housing half (Figures 1 to 18). 009816/0469
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