US2954917A - Electric swinging compressor - Google Patents

Electric swinging compressor Download PDF

Info

Publication number
US2954917A
US2954917A US626884A US62688456A US2954917A US 2954917 A US2954917 A US 2954917A US 626884 A US626884 A US 626884A US 62688456 A US62688456 A US 62688456A US 2954917 A US2954917 A US 2954917A
Authority
US
United States
Prior art keywords
armature
compressor
frequency
oscillating
piston
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.)
Expired - Lifetime
Application number
US626884A
Other languages
English (en)
Inventor
Bayer Friedrich
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.)
Licentia Patent Verwaltungs GmbH
Original Assignee
Licentia Patent Verwaltungs GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Licentia Patent Verwaltungs GmbH filed Critical Licentia Patent Verwaltungs GmbH
Application granted granted Critical
Publication of US2954917A publication Critical patent/US2954917A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F04B35/045—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric using solenoids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves

Definitions

  • This invention relates to compressors. More in particular, this invention relates to electro-magnetic oscillating compressors compressing gaseous substances used, for example in refrigerating systems and the like.
  • net frequency The frequency of the A.C. current available from the lines of a public electrical net shall be referred to hereinafter as net frequency.
  • the electrodynamic oscillatory impelling system suffers from the disadvantage of requiring two current sources for its operation, although the magnetizing DC. current can in some cases be replaced by permanent magnets. In addition, the amount of windings required is comparatively great. Furthermore, the quantitative yield as well as the degree of efiiciency are very low if these impelling systems are used for refrigerating compressors.
  • an equalization of the respective frequency of oscillation can be accomplished by mechanical means. This is achieved by providing the armature and the magnet poles with teeth and causing the armature to oscillate between neighboring, magnet pole teeth polarized in the same sense. In this case the oscillating, mechanical system must be tuned to this frequency. (Patent 2,351,6 3.)
  • the oscillating electro-mechanical system of the invention comprising, in combination, an electric impelling system, a magnetic system and a mechanical device to be impelled.
  • the mechanical device may consisnfpr example, of a compressor or a pump.
  • the magnetic system consists of a stator and an oscillator which is so arranged relative to the pole surfaces of the stator that an oscillatory movement results having a direction parallel to the polelsurfaces and which results in anoscillation, the amplitudev of which has no mechanical limitation.
  • the electric impelling system comprises a half wave rectifier and one or several exciting windings coiled; around the aforementioned stator of the magnetiesystem.
  • the entiresystem is operated by the half waves obtained from the half wave rectifier fed by an ordinary- A.C. current line.
  • the resting position of the oscillator must be so chosen that of two following half waves the first half wave moves the oscillator in the first end position and the second half wave moves the oscillator into the opposite, second end position. This is accomplished by providing one of the two members forming the magnetic system with teeth.
  • the difference of the number of the two members must be an odd figure and should preferably be 1.
  • care must be taken that the pole surfaces of the two members are not symmetrically congruent relative to one another during the resting position of the oscillator.-
  • the pole surfaces of the two members should preferably be so opposed that they do not cover each other.
  • the oscillator is adjusted to the desiredresting posi tion by resilient and preferably elastic means.
  • the oscillating mechanical system comprising the armature, the compressor piston and the resilient means are broughtto a natural frequency corresponding'approxirnatelyto half the net frequency.
  • the preferred embodimentof the electromechanical system of the invention consists of an oseill atingeom pressor having an electromagnetic impelling-system with poles and an armature which is provided with teeth; according to this preferred embodiment thedif Schlieren'ce-between the number of the teeth of the poles and the teeth of the armature is, 1 and if there is no current the ar-mature assumes a position relative to the poles that the teeth of the poles are facing the intermediate space between two neighboring teeth of the armature, hereinafter called interstice.
  • the displacement from the symmetrical resting position must be effected in the direction of the compression stroke.
  • the distance of the displacement depends upon the ratio of the width of the poles to the Width of the distance between the parts of the subdivided poles and the width of the opposite pole.
  • the energy of the resilient means must be adjusted in such a manner that in the absence of counter pressure the oscillator does not swing back beyond the symmetrical position of the pole having an inferior number of teeth in front of the interstioe of the pole having the greater number of teeth.
  • the compressor cylinder can be made to assume an elongated, configuration which is longer than the stroke produced by the oscillating impulsion would normally require.
  • the cylinder space can be divided into a cylinder space proper and an antechamber of a correspondingly smaller volume byan in tertnediate valve occupying the entire cross section of the cylinder and arranged. substantially at the point oftreversal of the piston at maximum pressure;
  • an intermediate valvegis'chosen which can-be pushed .forward -by the. piston in case of great amplitudes of oscillation.
  • Figure l is a diagram of; an electro-magnetic oscillat-. ing compressor of the invention, and its switch connections;
  • Figure :2 is a cross-section along the line II -tII in Figure 1 and shows the'poles and the armature of the compressor of the invention; a I
  • Figure 3 is a diagram showing the half wave fed to the exciting coil and the corresponding movement of the armature at various operational pressures
  • Figure 4 is a longitudinalsectional view of'a preferredembodiment of the apparatusof; the invention.
  • Figure 5 is a diagram illustrating the work performed bythec'ompressor of the apparatus shownin Figure. 4;
  • Figurev 6 is. a lateral view, partly'in section ofanother embodiment of the electromagnetic system of the. "ap-. par-atus oft'heainventiom' J Figure 7 isua lateral view partly in section of still another embodiment .of the electromagnetic timpelling rsys tem of the apparatus oftheinvention;
  • Figure 8 is a longitudinal sectional view .of' a further embodiment of the el'ectro-magnetic system of'the apparatusof theinyention; l
  • Figure 9 is a cross sectional view taken along the line IX-IX of the embodiment shown in Fig. 8;
  • Figure 10 is a diagrammatic lateral view of still another embodiment of the electro-magnetic impelling system of the invention.
  • Figure 11 is a diagrammatic view of the impelling system shown in Figure 10 as applied ,to a wing compressor with some modifications;
  • Figure 12 is a longitudinal sectional view taken along the line XII-XII of the Wing compressor shown in Figure 11;
  • Figure 13 is a cross-sectional view of the wing compressor shown along the line XIIIX[I'I in Figure 12;
  • Figure 13a shows an enlarged portion of the wing compressor shown in Figure 13;
  • Figure 14 is alongitudinal sectional view of a piston compressor with an electro-magnetic impelling system of the rotation-oscillating type, taken along the line XIV-XIV in Figure 15;
  • Figure 15 is a cross-sectional view of a piston compressor with an electro-magnetic impelling system of the rotation-oscillating type, taken along the line XV-XV in Figure 14;
  • Figure 16 is a sectional view of a piston compressor with an electro-magnetic impelling system of the rotationoscillating type, taken along the line XVI-XVI in Figure 15;
  • Figure 17 is a top view of the entire swing compressor of the embodiment of Figures 14 to 16.
  • Figure 1 shows the overall construction of the electro-mechanical system of the invention and its electrical wiring. If the apparatus of the invention is employed, for example, in refrigerators as a refrigerating compressor, the apparatus is housed in a hermetically sealed casing 1.
  • the entire system of the oscillating compressor is composed of a mechanical part and an electrical part.
  • the mechanical part is composed, for example of the compressor cylinder 2, the piston 7 moving within the cylinder 2, and the housing 3 consisting of a non-magnetic material.
  • the magnet frame 4 of the electromagnetic impelling system forming the second part of the entire system of the invention'
  • the magnet system is composed in a conventional manner of dynamo sheets and is equipped with two poles 5, 6 located opposite to each other. Each of the two poles 5, 6 is divided by an interstice or recess 5a and 6a respectively into two separate subpoles or teeth 5, 5" and 6', 6" respectively. Between these two poles, a disc shaped armature 9 serving as the oscillator is mounted upon the shaft 8 connected to the piston 7 of the compressor.
  • the armature is adjusted relative to the toothed poles 5, 6, by resilient means such as, for instance, springs 10, 11 in such a manner that in its position of rest the aramature faces the interstices 5a and 611 between the subpoles 5, 5", 6, and 6".
  • the springs 10 and 11 are so adjusted to the total mass of the combined armature 9, shaft 8 and the piston 7 that the entire movable mechanical system possesses a natural resonance frequency substantially corresponding to half the frequency of the exciting A.C. current.
  • the natural resonance is slightly inferior to half the frequency of the exciting A.C. cur rent, for reasons set forth further below.
  • the magnet system is excited by exciting coil means disposed about the legs of the magnet.
  • the exciting coil means may consist, for example, of two coils C5 and C6 connected in series.
  • the exciting current is supplied by the norm-a1 A.C. current network and an interposed half wave rectifier R. Any suitable type of rectifier can be employed. It will be found useful to use dry plate rectifiers, e.g. a selenium rectifier.
  • the exciting coil means is thus fed with half waves and receives 50 impulses of uniform direction per second if the net frequency is 50 cycles per second.
  • the approximate characteristic of these current impulses is shown by the upper curve in Figure 3 of the drawings.
  • the corresponding characteristic of the armature movements is shown by the lower curve of Figure 3.
  • Every impulse creates an electro-magnetic field between the poles of the magnetic system.
  • the two teeth of each pole 5 and 6 have identical polarity. If the armature 9 were to assume a position exactly between the teeth of the poles, the upper and the lower teeth would equally attract the armature and consequently the armature would 'retain its initial or zero position. For that reason the armature 6 is so adjusted in its position on shaft 8 as to assume a slightly asymmetrical position relative to the teeth 5', 6' on the one hand, and 5", 6" on the other hand. A very small degree of asymmetry is sufficient. If the armature 6 is positioned in this manner, the first current impulse will cause the armature to be attracted by the nearest couple of subpoles.
  • the nearest couple of subpoles should be the lower one, i.e. teeth 5" and 6" in Figure 1
  • the first half wave I (upper curve in Figure 3) will draw the armature in downward direction (see branch A of the lower curve in Figure 3).
  • the armature 9 will then bridge the air gap between the two lower teeth 5" and 6".
  • the armature will be moved in upward direction by force of the tension spring 11 (see branch B of the lower curve in Figure 3).
  • the kinetic energy stored in the armature 9 will make it swing through and beyond the substantially symmetrical resting or zero position and make it approach the zone between the upper teeth 5 and 6.
  • the lower curve in Figure 3 drawn in full lines corresponds to a pressure of approximately 4 atmospheres; the lower curve in Figure 3 drawn as a dashed line corresponds to a pres sure of approximately 6 atmospheres and the lower curve in Figure 3 drawn as a dashed-dotted line corresponds to a pressure of approximately 8 atmospheres in the compressorcylinder 2; all curves have been obtained on the basis of the example described in greater detail further below.
  • the armature performs one complete oscillation.
  • the feeding A.C. current has performed two periods.
  • the oscillatory compressor will perform 25 cycles 1). sec., ie, 1500 strokes p. min., if fed by an AC. current net of 50 cycles p. sec.
  • the resonance frequency is caused to approach the exciting frequency, as the load is increased and will coincide with half the net frequency when operated under full load. It has already beenmentioned further above, that an adjustment of resonance is advantageous in regard to the utilization of energy and conducive to obtaining sufficient oscillating amplitudes, but that, at the same time, it is accompanied by the difliculty of. providing excessively large amplitudes concurrently with a lack of counter pressure.
  • the particular construction of the magnetic system, the manner of excitation, as well as the adjustment of the oscillating parts offer a solution to overcome this drawback.
  • Figure 5 shows how, from this position, the armature 9 starts to oscillate within the range of the lower subpoles 5"and 6" with small amplitudes and at a frequency which is identical to the net frequency.
  • the small oscillations are continued until a sufiiciently elevated counter pressure has been created within the compressor cylinder 13a.
  • the small oscillating amplitudes are due to the fact that, as long as the oscillating frequency is identical to the net frequency, the mechanical system is not in resonance during this first part of the oscillation.
  • the counter pressure building up in the compressor cylinder 13a influences the armature 9 in the respective intervals between the occurrence of the half waves of the exciting current, and gradually displaces the zero position about which the armature 9 oscillates more and more away from its asymmetrical resting position. This continues until a zero position is reached which is situated closer to the upper subpoles 5' and 6' than to the lower subpoles 5" and 6", and the piston passes through that new zero position upwardly at a time when the following half wave starts to exercise its influence. Accordingly, the armature is pulled into the effective range of the upper subpoles. From this moment on, the armature executes large oscillating amplitudes at half the net frequency, in a part described further above.
  • the electrical part of the oscillatory compressor comprises a U-shaped magnet core 4 having poles 5 and 6 inwardly directed atthe ends of the legs 4a .and 4b.
  • the poles 5 and 6 are each composed of two subpoles 5 5" and 6', 6","respectively.
  • the .subpoles of each pole are, in turn, separated by recesses 5a and 6a, respec-.' tively.
  • the magnet core 4 preferably consists of laminations fabricated from a magnetic material known per se.
  • -The two poles 5 and 6' are opposed to and face. each other. Between them there is arranged a shaft 8.
  • armature 9 in such a manner that the shaft 8 and the armature 9 can move together freely in a vertical direction relative to the planes in which opposite subpoles extend.
  • armature 9 firmly upon the shaft 8
  • the latter being provided with a ledge-8a supporting the sheet metals of the armature 9.
  • the sheet metals forming the latter are held in position by a pressure disk 31 pressing firmly against the uppermost sheet and secured by a bolt 32-passing through the shaft 8.
  • the sheets are isolated from the shaft 8, for example, by an isolating layer 8b.
  • Shaft 8 is positioned, on the one hand, in a bore 12 which is provided in the basis of core 4 and, on the other hand, connected to the piston 7 of the compressor.
  • This piston 7 is guided inside the wall of the cylinder bore 13:: provided in the compressor casing 35.
  • the two poles 5 and 6 are each surrounded by an exciting coil C5, C6, respectively, connected in exactly the same manner as described above with regard to Figure .1.
  • the height hof the armature 9 corresponds approxi mately to the-width b of the subpoles 5', 5" and 6, 6.', respectively.
  • the recesses 5a and 6a between the subpoles measure approximately one and one half times the width of the subpoles.
  • the armature 9 is adjusted to adopt the required resting position by means of the two helical springs 10 and 1'1 surrounding the shaft 8 and each resting with its one end against the armature 9 and, with its respective other end, spring 10 against the yoke 40 of magnet core 4, and spring 11 against the compressor casing 35, respectively.
  • the armature 9 is located in this determined resting position, opposite to and facing the interstice between the'subpoles, but being displacedsomewhat towards the lower sub poles 5" and 6 so that its lower edge 9a is at a level with the upper edges 50, 6c of the lower pair of subpoles 5" and 6" or so that it is situated slightly above the level of the upper edges 50 and 6c.
  • the helical springs 10 and 11 are slightly tensioned while in their resting position. They are so adjusted to the other elements of the system as to form together with the armature 9, the shaft 8, and the compressor piston 7 an oscillating mechanical system having a natural frequency somewhat below the half frequency of the AC. current obtained from the main power network.
  • the casing 35 serves simultaneously as a carrier frame for the magnet system 4 and comprises the bore 13a being a part of the cylinder chamber 13.
  • This cylinder chamber 13 is elongated in a downward direction through a bore 13b in an intermediate piece 14 which is fastened to the lower end of the compressor casing 35.
  • This intermediate. piece 14 also provides the end wall .15 for the,
  • a spring loaded intermediate valve 16 is arranged parallel to the head surface 7a of the piston and covering the entire cross sectional area of the cylinder chamber 13; This intermediate valve divides the cylinder chamber 13 into the compression space proper (C) between the top surface 16a of the valve 16 and the head surface 7a of the reciprooating piston, and into a dampening space D between the lower surface 16b of the intermediate valve 16 and the cylinder end wall 15.
  • the intermediate valve 16 is arranged approximately at the level of the point of reversal of the piston at the highest required pressure and thus forms,in a manner. of speaking, a first, displaceable cylinder cover.
  • the intermediate valve 16 is adapted to be pushed downward ahead of the piston in case of large amplitudes of oscillation of the latter. This necessitates a graded configuration of the cylinder within the range of the dampening space, and, therefore, the intermediate piece 14 is provided with -a bore which is wider than the cylinder bore 13a.
  • the intermediate piece 14 further comprises an internal ledge 17 and an opening 10, therein the diameter of which opening corresponds to the diameter of the bore 13a.
  • the intermediate valve 16 rests against this ledge 17 and is pressed against the latter by the spring 19. It therefore functions like an ordinary pressure valve.
  • a suction valve 20 formed as a ring valve and clamped between the end surface 35a of the casing 35 and the intermediate piece 14.
  • the inclined front surface 17a of the intermediate piece 14 facing toward the cylinder bore 13a is recessed.
  • An annular groove 21 is cut into the end surface 35a of the casing 35 and is connected via the intake channel 22 with an intake conduit for the gas to be compressed (not shown).
  • the compressor is located within a hermetically sealed casing (not shown in Figure 4) subjected to suction pres sure (see Figure l), wherefore the intake channel is connected only with the interior of the sealed casing.
  • the suction intake valve 20 formed by a ring plate which is clamped at its outer margin between end surface 35a of the casing 35 and the intermediate piece 14, rests resiliently against the annular groove 21; spring means are not re quired because of the tensioning of the valve as a diaphragm.
  • the inner diameter of this annular valve is somewhat larger than the diameter of the piston, and the piston can therefore pass through the valve.
  • the suction valve can also be arranged laterally in the wall of the cylinder or in the bottom of the piston as an ordinary plate valve. In the latter instance the gas to be compressed can be conducted through the hollow shaft of the piston and the armature (see Patent 2,054,097).
  • the cylinder end wall 15 is connected via a central bore 23 to the lower end surfacel4a of piece 14.
  • the pressure valve 27 is pressed by a comparatively strong spring 29 against the end surface 14a to close the bore 23, and normally shuts off the cylinder and dampening space against the pressure conduit 26.
  • the space enclosed in the cap 28 communicates with the interior of the outer casing 1 of Figurel through a bore 30.
  • the diaphragm forming valve 27 is, therefore, under the influence of the suction pressure prevailing in that external casing.
  • the tensioning of the pressurev valve effected by the spring 29 is so chosen, that the piston 7 must work against a determined minimum bias pressure. The amount of this bias pressure depends on the demanded work pressures and will be in the order of 3 atmospheres at the normal Working pressure of from 6 to 8 atmospheres.
  • the armature swings back as it is influenced primarily by the energy of the spring 11. Since, with the exception of the pressure in the dampening space, there is as yet no counter pressure built up in the compressor, the armature swings only a very short distance beyond the resting position and, accordingly, the next following magnetic impulse again draws the armature downwardly, because, at the moment at which this impulse takes effect, the armature is still closer to the lower pair of subpoles than to the upper pair.
  • the armature thus oscillates at the frequency of the exciting half wave, e.g. with a 50 cycle A.C. current, it oscillates at a frequency of 50 cycles p. sec.
  • the mounting pressure first in the dampening space and, after the tensioning of the pressure valve has beenovercome, also in the remaining parts of the system, gradually incites the armature during the following current intervals and because of the resulting counter pressure on piston 7, to swing back more and more beyond its resting position until, finally, the armature swings beyond the symmetrical position between the pole shoes 5 and 5", and 6' and 6" respectively.
  • the zero position through which the armature passes at each oscillation is thereby shifted closer to the upper pair of subpoles 5', 6' than to the lower pair of subpoles, and, at the commencement of subsequent impulses, the annature is consequently attracted by the upper pair of sub: poles.
  • the time needed for the change of oscillation-terse in depends upon the size of the dampening spacera nd the correspondingly adjusted counter pressure. 'In the example described, this time .does not exceed a:few..seconds.
  • the course of the oscillations of ith'earmature from the start to full operation .is demonstratedbyxthe time-distance curve in Figure 5.
  • both the starting oscillations at net frequency and the dampening space. with its minimum pressure contribute essentially to prevent the pis-' ton from hitting the intermediate valve forming the cover of the cylinder chamber C.
  • the piston 7 may-advance well into the cylinder bore 13b in piece 14, as long-as the maximum pressure of operation has not yet been attained, and the amplitude of oscillation is correspondingly great. In doing so, the piston 7 pushes the intermediate valve ahead of it "in a downward direction. However, the counter pressure and the gas cushion forming 'betweemthe bottom of the piston and the plateshaped intermediate valve prevent the piston from hitting the intermediate valve abruptly and with excessive force. Thus, any damage to the intermediate valve is avoided and undesirable noise is eliminated.
  • the subpoles have a width'of -13 mm., the recess between every two subpoles is 21 mm. wide, the width of the armatureis 14 mm.
  • the total weight of the oscillating masses attains approximately 300 grams.
  • the adjustment and adaptation to resonance is effected by twohelical springs each having a length of 70 mm. and having a spring constant of Z 3.1 kg./cm.
  • the armature is so adjusted that its lower edge protrudes 0.5 mm. from the lower edge of the lower pair of subpoles.
  • the natural frequency can be reduced from, for instance, a half frequency of 25 cycles of the AC. current supplied by the net down to cycles during idling.
  • the exciting coils had 600 windings each and a diameter of the coil wire of 0.7 mm.
  • the current received was 1.5 amp. at a frequency of 50 cycles and 1.2 amp. at a frequency of 25 cycles.
  • the integrated power absorption of 55 :to watts was therefore surprisingly low.
  • Figure .6 shows schematically a magnet system comprising a compressor housing 43, a magnet frame 44, the poles 45, 46 of which are undivided and each carry one exciting coil C45 and C46 respectively.
  • armatures 49', 49" Upon the. shaft .48 of the armature there are mounted 2 disk-shaped armatures 49', 49" at such a distance from each other that the interstice 49a between them is situ- I ated in the resting position exactly opposite the stator magnet poles 45 and 46.
  • the upper armature 49' must be positioned at a smaller distance from the stator poles 45 and 46 than the lower armature 49".
  • two helical springs '50, 51 effect the adjustment and adaptation of the system.
  • the poles and the armatures may be further subdivided.
  • two armature disks 59' and 59" face the interstices of three stator pole teeth 55a, 55b, 550 of stator pole 55 and teeth 56a, 56b, 560 of the opposite stator pole 56.
  • the positioning of the armature in front of the interstices must be carried out exactly in the manner shown in Figure 4.
  • Figure 7 also shows that the adjustment and adaptation can be carried out by means of a helical spring 61 the ends of which are fastened at 62a to the armature disk 59 on the one hand, and to the compressor casing '53 at 62 on the other hand.
  • the spring 61 can be subject to pressure as well as to tension.
  • the exciting coil means need not be divided into separate coils for each pole as indicated in the previous examples; it is suflicient to use one single exciting coil C7, as shown in Figure 7, and to mount this coil on the yoke 54a of the U-shaped magnet core 54.
  • the compressor cylinder 53a is enclosed in the casing 53.
  • the oscillating system is guided in straight direction solely by means of the elongated compressor piston 57 reciprocating in cylinder 530.
  • the magnet frame is so arranged that its central plane i.e. the plane defined by the magnetic flux circuit, coincides with the plane determined by the axis of oscillation of the oscillator. It is also possible to have the axis of oscillation positioned vertically relative to the central plane of the magnet frame. This is the case in the magnet system shown in cross section in Figure 8 and in longitudinal section in Figure 9.
  • reference numeral 74 identifies the magnet core
  • 73 designates the compressor casing with the cylinder "(not shown)
  • 78 refers to the oscillatory shaft
  • a non-magnetic yoke 73a is fixedly attached to the magnet core 74 and acts as a guide means for the oscillatory shaft 78.
  • FIG. 10 Another modification is shown in Figure 10.
  • the armature 69 revolves around its shaft 68 and its surfaces facing and opposed to poles 65, 66 of the magnet frame 64 are provided with teeth 69', 69".
  • the exciting coils C65 and C66 are mounted uponthe legs of the U-shaped magnet frame 64.
  • the adjustment of the armature is effected, for instance, by means of two springs 70, 71 each acting with their one end upon the arm 69c of the armature 69. Their respectiveother ends are attached to casing 63.
  • the interstices 69a between the teeth of each pair 69 and 69" are situated opposite to the poles 65 and 66 of the magnet frame.
  • the adjustment of the springs 70 and 71 can be made to be asymmetrical and the oscillatory mechanical system is simultaneously, adjusted to half the exciting frequency. After starting at the exciting frequency, the system automatically changes to half the exciting frequency after a short period.
  • the compressor is preferably of the type of a wing or wing piston compressor (not shown) and it is connected with the revolving axis shaft 68.
  • the U-shaped magnet core 84 has two poles 85 and 86, each having two subpoles 8'5, 85" and 86, 86 subdivided by the interstices 85a and 86a.
  • the armature 89 is fixedly mounted upon the shaft 88 to be rotated therewith and it is located between the surfaces of the poles 85 and 86 facing each other.
  • the exciting coil 82 is wound around the yoke of the U-shaped core; Shaft 88 is formed by a torsion bar and thus replaces the springs usually needed for the adjustment of the resting position and the adaptation to resonance of the system.
  • shaft 88 is firmly clamped in a socket 81 with its free left end (see Figure 12).
  • This socket constitutes a part of the frame of the frame 83 which is connected at one of its ends with the magnet core 84 in a manner known per se.
  • the other end of the frame 83 supports the casing 90 of a wing compressor.
  • the frame can be adapted to form a uniform structure with the compressor casing 90.
  • the casing 90 is provided with two small bridges 94 reaching to the basis of the U-shaped core and firmly attached to the latter.
  • this particular construction of the frame and the modes of attaching the same to the compressor and the impelling magnet are not considered parts of the present invention.
  • the torsion shaft 88 is clamped in socket 81' at its left, free end, and its right end is prolonged beyond the armature and bears the revolving piston 91.
  • the r'evolving piston 91 has two wings 91a and 91b and moves within the cylindrical compressor space 93 of the compressor casing 90.
  • the compressor space 90 is covered by the cylinder covers 95 and 96 at those ends which are connected, for instance by screw connection, to the casing 90.
  • Two valve bodies 92a and 92b containing the pressure valves 97 are arranged within the compressor space in diametrical position relative to each other. They are fixedly connected with at least one of the. cylinder covers 95, 96.
  • valve bodies will be clearly recognized from the enlarged view thereof shown in Figure 13a.
  • the wing compressor The suction conduits 98 and the pressure conduits 99 serve for the connection of the respective pipes which are connected to the com- 14 pression system, for instance a refrigerating installation, in a generally known manner.
  • the armature 89 is mounted upon the shaft 88 in a position in which its poles 89a and 89b are located opposite to and facing the interstices a and 86a, if the torsion shaft is de tensioned; the position of the armature 89 relative to the interstices 85a, 86a is somewhat asymmetrical in order to facilitate the first oscillations.
  • FIGS 11 to 13a show another position, namely the compression end position in which the poles of the armature are located in front of one of the pairs of subpoles of the magnet systemand in which the wings 91a and 91b are positioned close in front of the valve bodies 92a and 92b, respectively.
  • the system operates as follows: In the resting position the armature '89 stands facing the interstices 85a, 86a between the magnet subpoles, and the wings 91a and 91b of the compressor assume a horizontal position. Upon exciting the coils with half waves, the armature will be brought to the indicated position by the first half wave. The rotary piston 91 now turns counterclockwise and compresses the gas within the compression space located in front of the piston and into which the gas has been pressed via the valve bores 97a in the valve bodies, the pressure valves 97 and the pressure channels 99.
  • the orifices of the suction channels 98 are rendered accessible shortly after the commencement of the operation, and by the following movements the gas is sucked through these channels into the space behind the wings.
  • the suction pipes are provided with suction valves in a conventional manner in order to prevent the sucked gas from being pushed back into the suction channels during the return movement of the wings.
  • these suction valves are not shown.
  • the return movement of the wings back to their initial resting position, after the exciting half wave has subsided, is effected by the detensioning of the torsion shaft 88 originally tensioned by the first movement of the armature.
  • the exciting coil is mounted close to the poles upon the magnet frame 84.
  • the magnet frame 84 is connected with a frame 103 which is U-shaped and has two legs 103a and 103b, the latter forming the bearings for the shaft 88 of the armature 89, on both sides of the magnet system.
  • a three-armed T-shaped lever 104 is firmly connected with the axis 88 and provided with a downwardly extending leg 104a provided at its lower end with an elongated slot 105.
  • the lower end of the lever is embraced by the fork-shaped end 1061: of the piston rod, or-as shown in the drawingsthe compressor 15 piston 106 itself.
  • the compressor piston 106 cooperates with the cylinder 108, the latter being shut by the cylinder cover 109 containing the pressure valve and the suction valve in the usual manner.
  • the two substantially horizontally extending legs and 104a are recessed at the back of'their respective lower ends at 112 and 113,. each recess receiving the ends of two helical springs 110 and 111 respectively. The other ends of these springs rest against corresponding protrusions IE4 and 115 respectively, of the cylinder 198 and the frame .103, respectively. These springs adjust the armature to its resting position, reset the same and adapt the entire oscillating mechanical system to the resonance frequency corresponding to half the exciting frequency.
  • Figures 14 to 17 show the entire construction in a position corresponding to the end of the suction stroke.
  • This construction operates in the samemanner as decribed for the example shown in Figure 10 as to the electrical operation, and as described for the example shown in Figure 4 as to the compressing operation.
  • the invention has proved to be particularly useful if applied to refrigerating compressors-in refrigerators md especially household refrigerators.
  • the invention offers a simple, sturdy and particularly noiseless compressor having a long life time and consuming a minimum of energy.
  • an electro-mechanical system combining an electro-magnetic oscillating system comprising a stationary I electro-magnetic member, an oscillating member, and pole means associated with each of said two mnembers and comprising pole portions facing each other, with a fluid-conveying mechanical machine driven by saidoscillating member the combination of rectifying means for exciting said oscillating system with half waves derived from an electrical alternating current source, a plurality of pole portions forming the pole means of at least one of said two members, the difference between the number of pole portions associated with each of said two members being one, means for maintaining said oscillating member when at rest, in such a position relative to said stationary electro-magnetic member that the pole teeth of the pole means of one of said members face the interstices between the pole teeth of the pole means of the other of said members, the first of saidhalf waves thus forcing said oscillating member into the first end position and the following of said half waves forcing said oscillating member into the second end position, and means-for adjusting the oscillating system
  • intermediate valve said intermediate valve being arranged within said elongated cylinder at the point of reversal of said piston, said intermediate valve dividing the interior space of said elongated cylinder into a compression space in which said piston shuttles back and forth and 'a dampening space, further comprising a presi6 sure valve, said pressure valve shutting said dampening space. against said pressure pipes except for a minimum pressure allowed within said dampening space and against which the piston has to act.
  • An electro-rnechanical system comprising, in combination: an electro-magnetic oscillating system comprising a stationary electro-magnetic member, an oscillating member, pole teeth connected with one of said two members, and spaced pole portions which face each other to form an interstice andwhich are connectedwith the other of said two members; a mechanical fluid conveying device driven by said oscillating member and having an operational frequency equal to that of said oscillating member; means for exciting said oscillating system with half waves derived from an electrical alternating current source, said oscillating system being adjusted to a natural resonant frequency equal to approximately half the frequency of the alternating current source; and means for resiliently maintaining said oscillating member, when at rest, in such a position relative to said stationary electro-magnetic member that said pole teeth of said one member are arranged asymmetrically in said interstice between said facing pole portions of said other member sothat when said exciting means excite said oscillating system, said pole teeth of said one member and said facing pole portions of said other member are displaced

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
US626884A 1955-12-07 1956-12-07 Electric swinging compressor Expired - Lifetime US2954917A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE1162026X 1955-12-07

Publications (1)

Publication Number Publication Date
US2954917A true US2954917A (en) 1960-10-04

Family

ID=7728518

Family Applications (1)

Application Number Title Priority Date Filing Date
US626884A Expired - Lifetime US2954917A (en) 1955-12-07 1956-12-07 Electric swinging compressor

Country Status (4)

Country Link
US (1) US2954917A (da)
AT (1) AT194870B (da)
DK (1) DK87310C (da)
FR (1) FR1162026A (da)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3461806A (en) * 1965-03-12 1969-08-19 Maurice Barthalon Reciprocating electric motor
US3485441A (en) * 1966-09-28 1969-12-23 Texas Gas Transmission Corp Magnetically biased compressor check valves
US3947155A (en) * 1974-09-19 1976-03-30 Tecumseh Products Company Linear compressor
US4518317A (en) * 1982-08-12 1985-05-21 Inoue-Japax Research Incorporated Fluid pumping system
US4883467A (en) * 1987-04-22 1989-11-28 Siemens Aktiengesellschaft Reciprocating pump for an implantable medication dosage device
US5597294A (en) * 1993-06-02 1997-01-28 Pegasus Airwave Limited Electromagnetic linear compressor with rotational bearing between springs
US20060216170A1 (en) * 2005-03-28 2006-09-28 Nitto Kohki Co., Ltd. Electromagnetic reciprocating fluid apparatus
US20070286751A1 (en) * 2006-06-12 2007-12-13 Tecumseh Products Company Capacity control of a compressor
US20080240950A1 (en) * 2003-05-30 2008-10-02 Mcgill Ian Campbell Compressor improvements
US20120177513A1 (en) * 2009-07-08 2012-07-12 Whirlppol S.A. Linear compressor
US20140234145A1 (en) * 2011-07-07 2014-08-21 Whirlpool S.A. Arrangement of components of a linear compressor
US20140301874A1 (en) * 2011-08-31 2014-10-09 Whirlpool S.A. Linear compressor based on resonant oscillating mechanism
US20170373576A1 (en) * 2016-06-23 2017-12-28 Lg Electronics Inc. Transverse flux reciprocating motor and reciprocating compressor having a transverse flux reciprocating motor

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2446394A1 (fr) * 1979-01-10 1980-08-08 Matoba Tsuyoshi Compresseur, notamment pour installations de conditionnement d'air
DE9413744U1 (de) * 1994-08-25 1995-09-21 Siemens Ag Anordnung zum Steuern der Leistung eines Schwingankerantriebs

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1637401A (en) * 1927-08-02 Best available cop -
DE596890C (de) * 1932-08-21 1935-03-18 Wilhelm Koenig Dipl Ing Antrieb fuer Kleinkompressoren, insbesondere fuer Kaeltemaschinen
US2054097A (en) * 1932-05-31 1936-09-15 James B Replogle Harmonic compressor
US2180189A (en) * 1934-10-13 1939-11-14 Central Electric Tool Company Vibrator
CH208419A (de) * 1937-11-01 1940-01-31 Hermes Patentverwertungs Gmbh Elektrodynamischer Schwingantrieb für Arbeitsmaschinen, beispielsweise Siebe.
US2194535A (en) * 1937-04-15 1940-03-26 Vedee Corp Electric translating device
US2297025A (en) * 1941-07-14 1942-09-29 George W Russell Air pump
US2351623A (en) * 1941-07-29 1944-06-20 Martin Brothers Electric Compa Oscillating electric motor
US2481147A (en) * 1947-09-18 1949-09-06 Bendix Aviat Corp Reciprocating electromagnetic motor
US2488723A (en) * 1947-11-10 1949-11-22 Autopulse Corp Electromagnetic motor

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1637401A (en) * 1927-08-02 Best available cop -
US2054097A (en) * 1932-05-31 1936-09-15 James B Replogle Harmonic compressor
DE596890C (de) * 1932-08-21 1935-03-18 Wilhelm Koenig Dipl Ing Antrieb fuer Kleinkompressoren, insbesondere fuer Kaeltemaschinen
US2180189A (en) * 1934-10-13 1939-11-14 Central Electric Tool Company Vibrator
US2194535A (en) * 1937-04-15 1940-03-26 Vedee Corp Electric translating device
CH208419A (de) * 1937-11-01 1940-01-31 Hermes Patentverwertungs Gmbh Elektrodynamischer Schwingantrieb für Arbeitsmaschinen, beispielsweise Siebe.
US2297025A (en) * 1941-07-14 1942-09-29 George W Russell Air pump
US2351623A (en) * 1941-07-29 1944-06-20 Martin Brothers Electric Compa Oscillating electric motor
US2481147A (en) * 1947-09-18 1949-09-06 Bendix Aviat Corp Reciprocating electromagnetic motor
US2488723A (en) * 1947-11-10 1949-11-22 Autopulse Corp Electromagnetic motor

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3461806A (en) * 1965-03-12 1969-08-19 Maurice Barthalon Reciprocating electric motor
US3485441A (en) * 1966-09-28 1969-12-23 Texas Gas Transmission Corp Magnetically biased compressor check valves
US3947155A (en) * 1974-09-19 1976-03-30 Tecumseh Products Company Linear compressor
US4518317A (en) * 1982-08-12 1985-05-21 Inoue-Japax Research Incorporated Fluid pumping system
US4883467A (en) * 1987-04-22 1989-11-28 Siemens Aktiengesellschaft Reciprocating pump for an implantable medication dosage device
US5597294A (en) * 1993-06-02 1997-01-28 Pegasus Airwave Limited Electromagnetic linear compressor with rotational bearing between springs
US8684706B2 (en) * 2003-05-30 2014-04-01 Fisher & Paykel Appliances Limited Connecting rod for a linear compressor
US20080240950A1 (en) * 2003-05-30 2008-10-02 Mcgill Ian Campbell Compressor improvements
US20060216170A1 (en) * 2005-03-28 2006-09-28 Nitto Kohki Co., Ltd. Electromagnetic reciprocating fluid apparatus
US7932647B2 (en) * 2005-03-28 2011-04-26 Nitto Kohki Co., Ltd. Electromagnetic reciprocating fluid apparatus
US20070286751A1 (en) * 2006-06-12 2007-12-13 Tecumseh Products Company Capacity control of a compressor
US20120177513A1 (en) * 2009-07-08 2012-07-12 Whirlppol S.A. Linear compressor
US8998589B2 (en) * 2009-07-08 2015-04-07 Whirlpool S.A. Linear compressor
US10221842B2 (en) 2009-07-08 2019-03-05 Whirlpool S.A. Linear compressor
US20140234145A1 (en) * 2011-07-07 2014-08-21 Whirlpool S.A. Arrangement of components of a linear compressor
US9562526B2 (en) * 2011-07-07 2017-02-07 Whirlpool S.A. Arrangement of components of a linear compressor
US20140301874A1 (en) * 2011-08-31 2014-10-09 Whirlpool S.A. Linear compressor based on resonant oscillating mechanism
US9534591B2 (en) * 2011-08-31 2017-01-03 Whirlpool S.A. Linear compressor based on resonant oscillating mechanism
US20170373576A1 (en) * 2016-06-23 2017-12-28 Lg Electronics Inc. Transverse flux reciprocating motor and reciprocating compressor having a transverse flux reciprocating motor
US10862383B2 (en) * 2016-06-23 2020-12-08 Lg Electronics Inc. Transverse flux reciprocating motor and reciprocating compressor having a transverse flux reciprocating motor

Also Published As

Publication number Publication date
FR1162026A (fr) 1958-09-08
DK87310C (da) 1959-05-19
AT194870B (de) 1958-01-25

Similar Documents

Publication Publication Date Title
US2954917A (en) Electric swinging compressor
US3991585A (en) Cold-gas refrigerator
KR102259650B1 (ko) 리니어 압축기
JP2005344708A (ja) 往復動圧縮機及びその駆動装置並びに制御方法
KR102333982B1 (ko) 리니어 압축기
KR102244373B1 (ko) 리니어 압축기 및 리니어 모터
JPS61126385A (ja) 振動型圧縮機
JP4195389B2 (ja) 往復動式圧縮機
JP2005256833A (ja) リニア圧縮器
KR20150077155A (ko) 왕복동식 압축기
US2351623A (en) Oscillating electric motor
US2605042A (en) Electromagnetically driven selfregulating fluid compressor for use in refrigerating machines
US3075471A (en) Pump and operating means
JP2004519585A (ja) 往復動式圧縮機
JP4599881B2 (ja) 密閉型圧縮機
GB905095A (en) Improved electro-magnetic compressor
KR200147722Y1 (ko) 리니어압축기
KR102122097B1 (ko) 리니어 압축기
KR102162335B1 (ko) 리니어 압축기
KR100597295B1 (ko) 리니어 압축기
GB874489A (en) Improvements in or relating to electro-magnetically driven pumps
KR20090041706A (ko) 리니어 압축기
KR100253214B1 (ko) 압축기의 리니어 모터 구조
RU2142576C1 (ru) Компрессор кинетического сжатия и объемного нагнетания с магнитоэлектрическим приводом
KR100673735B1 (ko) 리니어 압축기의 냉매 압축 방법