DE69823533T2 - LINEAR MOTOR COMPRESSOR - Google Patents

Description

technical Field of the invention

These The invention relates to a linear motor and a compressor in which such a motor is installed.

background the invention

The This invention provides improvements in UK Patent No. GB2299715B disclosed invention. A piston type linear motor compressor is in U.S. Pat. No. 4,613,285, which serves as a basis for the Preamble of the claims 1 and 2 to define.

Summary the invention

One The first object of the invention is to provide a linear motor and / or compressor with improved energy efficiency and a more compact and cost-efficient structure.

According to one Aspect of the invention, a linear motor is provided, comprising: a stator, a reciprocating member, and means for moving the stator and / or to apply energy to the reciprocating element; wherein the stator Magnetic flux generating means which are arranged so that a Variety of axially exposed magnetic air gaps is formed, and the reciprocating member comprises magnetic flux generating means which are formed so that they have a variety axially exposed Magnetic air gaps form to by thrust-and-pull forces with to interact with the magnetic air gaps of the stator.

According to one Another aspect of the invention provides a linear compressor, comprising: a housing, which encloses a stator, the defines an interior, a reciprocating element, that in the interior is arranged, means to the stator and / or the Hubkolbenelement to energize, as well as valve means to at least one Fluid passage in and out of the interior to form; and in which the stator comprises magnetic flux generating means arranged to form a plurality of axially exposed magnetic air gaps, and the reciprocating member has magnetic flux generating means, which are arranged to a plurality of axially exposed magnetic air gaps to form, by thrust-and-pull forces to interact with the magnetic air gaps of the stator.

It is beneficial, a series of magnetic air gaps between the stator and the runner along the operating axis of the runner to arrange so that the diameter of the stator and the rotor are reduced can. It is also advantageous, the pole means of the stator and the runner in an intermediary relationship, so not only this the push and pull drive forces, but also improves the electromagnetic suspension effect on the runner, which increases the energy efficiency and the on the Suspension springs acting operating load is reduced. Preferably the stator windings are divided into two or more groups, and in their electricity flows becomes a phase difference to further increase the suspension effect introduced.

Becomes for one certain application a stronger one Driving force needed, this can be done simply by arranging more magnetic air gaps along the Stator and rotor structure, causing a longer and more powerful Unit is formed, achieved. Such a relatively narrow one and long construction ensures better heat radiation, what kind of a high performance unit is extremely beneficial, especially when these temperature sensitive rare earth magnets starts.

It is preferred that the rotor element of a central guide device is worn to its non-contact To ensure movement relative to the stator, and to a sealing gap to form, which allows a lubricant-free operation. The central guiding device can a hollow shaft extending through the reciprocating element be through a coolant to let this circulate. Alternatively, the central guiding device from a pair of coaxially aligned shafts with the reciprocating element worn pistons exist.

Also the formation of a multi-stage compressor arrangement is preferred by dividing the space inside the compressor into a pre-compression space and another compression space, allowing a process fluid level can be compressed by level. It would be advantageous to form a gap to obtain the compressed fluid from the Vorkompressionsraum to to cool this and then forward to the other compression room. It is an advantage, the compression chambers the second stage outside the linear motor structure to arrange the heat radiation and the energetic Increase efficiency.

It is preferred, an improved suspension mechanism for the reciprocating element in To provide a linear motor, so the operation of the engine more efficient and reliable close.

It is advantageous to have a suspension mechanism for the reciprocating element in a linear motor, wherein the linear motor has a stator with pole means to interact with the pole means on the reciprocating member to cause the latter to reciprocate between two end positions; and wherein the suspension mechanism comprises a magnetic spring means disposed so as to interact with the pole means on the reciprocating member to produce a return force in response to its movement toward the end position.

Preferably the magnetic spring means has a nested permanent magnet structure which forms an internal flux concentration with the reciprocating element to act when this enters the structure. Alternatively the magnetic spring means consists of an electromagnet with axial exposed magnetic gap to act with the Hubkolbenelement.

It is preferred, a linear motor with a device for flow switching to make the engine operation more efficient.

It It is advantageous to have a flow switching mechanism for one Linear motor, over a stator having a plurality of magnetic flux gaps defining Polmittel has, to interact with the Polmittel on a Hubkolbenelement wherein the pole means of the stator is a Flow switching means for switching the magnetic flux towards one of the directions of an excitation current supplied to the stator, corresponding axial direction includes the magnetic coupling between the stator and Hubkolbenelement to reinforce.

Preferably In addition, the stator pole means have an axial direction extending pole face expansion structure to further increase the magnetic coupling.

It is preferred, a linear motor and / or compressor with a suspension mechanism to provide vibration-free operation.

It is an advantage, a linear motor and / or compressor with a casing providing a stator and a reciprocating member (rotor), wherein both stator and reciprocating element are suspended, around them relative to the case to make it movable, so that the interaction between Stator and Hubkolbenelement a movement of these in opposite directions triggers.

Preferably the stator is suspended with a Belleville washer, the also its precise Alignment with the housing guaranteed. It is advantageous that the disc spring means also as a membrane agent acts, which divides the space between the stator and the housing into spaces, so that the movement of the stator also produces compression effects.

Summary the drawings

The Features, advantages and details of the invention will be made with reference to the preferred embodiments, which in the attached Drawings are illustrated, in which:

1A and 1B Cross-sectional views along the central axis of a compressor according to a first preferred embodiment of the present invention;

2 Fig. 10 is a sectional view showing static parts of the first embodiment;

3 a sectional view of a rotor in the first embodiment;

4A and 4B Cross-sectional views along the central axis of a compressor according to a second preferred embodiment of the present invention;

5 Fig. 10 is a sectional view showing static parts of the second embodiment;

6 a sectional view of a rotor in the second embodiment;

7 Fig. 12 is a cross-sectional view taken along the center axis of a compressor according to a third preferred embodiment of the present invention;

8th Fig. 10 is a sectional view showing static parts of the third embodiment;

9 Fig. 10 is a sectional view of a rotor device in the third embodiment;

10 represents a control circuit for the third embodiment;

11 Fig. 12 is a cross-sectional view taken along the center axis of a compressor according to a fourth preferred embodiment of the present invention;

12 Fig. 10 is a sectional view showing static parts of the fourth embodiment;

13 Fig. 10 is a sectional view of a rotor device in the fourth embodiment;

14A to 14E illustrates the working principle of a flow switching mechanism;

15 Fig. 10 illustrates a control circuit for the fourth embodiment of the present invention;

16A and 16B Cross-sectional views along the central axis of a compressor according to a fourth preferred embodiment of the present invention;

17 Fig. 10 is a sectional view of a housing structure of the fifth embodiment;

18 Fig. 10 is a sectional view of a stator in the fifth embodiment;

19 Fig. 10 is a sectional view of a rotor device in the fifth embodiment; and

20A and 20B illustrates the structure of a reed valve.

detailed Description of the Preferred Embodiments

In This application is for the purpose of better understanding the invention described as a compressor. It should be, however Understand the same concept for gases as well as for liquids also for a vacuum pump can be used. The term "compressor" should accordingly as all these applications are understood to be covering, except it will explicitly said something else. The same concept can be used to build a Linear motors are used by simply the valves and seals be omitted. For this reason, there is no need for one own description for it, like the individual embodiments a compressor for be modified a linear motor. Furthermore, he is in this Application used term "magnetic Arrangement "as designation for everyone To understand arrangement for generating a magnetic flux including Electromagnets, permanent magnets or a combination of both. Once the working principle has been explained, there is no need for it be noted that an exchange of one type of the "magnetic arrangement" with the other or a combination of both is of course possible. Finally is It is obvious that an efficient engine design by reverse Commissioning, d. H. by using a mechanical drive power, can also be used as a power generator.

General Structure of the first embodiment

In 1A has a compressor 10 over a housing 20 , two annular electromagnets 40 and 40 ' , which are attached to two ends of the building, two short shafts 30 and 30 ' (not shown in cross section), each of which is fitted in the center of an electromagnet, a rotor element carried by the short shafts 50 and a coil spring 61 and 61 ' and damping magnets 62 and 62 ' comprehensive suspension mechanism. The two electromagnets 40 and 40 ' are similar to the inventor's UK Patent No. GB-2299715-B for producing a runner 50 acting thrust-and-pull force arranged.

The compressor 10 is a double-acting unit with an internal, multi-stage compression assembly that includes three pairs of separate chambers between the rotor 50 and the electromagnet 40 and 40 ' are formed. More specifically, two first stage compression spaces I and I 'form the annular spaces between each of the axial ends of the rotor 50 and a damping magnet 62 or 62 ' into which the process fluid from outside the compressor via the channels 70 and 70 ' is introduced. Two compression chambers of the second stage are defined by the cylindrical spaces II and II 'inside the rotor 50 formed, in which the process fluid from the rooms I and I 'by means of the channels 80 and 80 ' is introduced. Two further rooms G and G 'are the annular spaces around the pole shoes 54 and 54 ' and form gas springs as part of the rotor's suspension mechanism.

In 2 has the housing 20 via a non-magnetic cylindrical wall 21 with a number of outer ribs 22 for better mechanical strength and heat dissipation. The two electromagnets are identical, so here only the right one 40 is described. The corresponding parts of the left electromagnet 40 ' are identified by the same reference numbers with apostrophe '.

The electromagnet 40 has a magnetic base element 41 that by fastening means 23 on the housing 20 is appropriate. Its magnetic circuit is through an annular outer pole piece 42 that with the base 41 by means of a magnetic element 43 is connected, and a coaxial inner pole piece 44 , which is directly connected to the base at the rear end, formed. A toroidal coil 45 is in the ring-shaped, of the elements 42 . 43 . 41 and 44 fitted room. An axially releasing magnetic air gap is between the pole pieces 42 and 44 for interaction with the pole piece of the rotor, as will be described below, formed.

Between the two electromagnets is a separating ring 24 , made of a nonmagnetic, thermally conductive material, such as brass or aluminum, to improve the heat The discharge of the compressor is trapped. A non-magnetic lining element 25 is inside the ring 24 fitted, which extends into the magnetic air gaps of the two electromagnets. That means that the lining element 25 forms a complete and smooth inner surface, which fits tightly to the outer surface of the runner 50 so that when the distance between the two is about 10 microns, a sealing gap is formed, which prevents the escape of gas through the same. The two end portions of the lining element 25 also define the outer wall of the gas spring spaces G and G '. The inner pole shoe 44 has a lining element on its inner surface 46 , which forms the outer wall of Vorkompressionsraums I.

The two shafts 30 and 30 ' are aligned axially to guide the movements of the rotor. The two are identical, whereby only one, ie the right one 30 , is described here. The shaft 30 has a tubular section 31 , a piston head 32 , fitted in one end of the section 31 , a one-way valve 34 in the piston head and a seal 33 on the outer surface of the piston head. The seal 33 is for lubricant-free operation of a self-lubricating material, such as Teflon (registered trademark), manufactured.

Structure of the runner

In 3 points the runner 50 an annular middle magnet 51 which is radially magnetized, ie its outer edge region is the north pole (the outer pole) and its inner edge region is the south pole (the inner pole), so that its outer surface generates a uniformly distributed over its entire circumference radial magnetic flux to the annular Poland electromagnets to act. A magnetic, tubular element 52 is inside the ring-shaped magnet 51 fitted and serves as its inner pole piece.

Two intermediate pole shoes 54 and 54 ' are each at one end of the tube 52 fitted and at its axial ends are two end magnets 55 and 55 ' which are axially magnetized. The polarity of the magnets is aligned so that the pole piece 54 or 54 ' magnetic with the south pole of the middle magnet 51 and that of the end magnet 55 or 55 ' connected, creating a highly concentrated magnetic flux for acting with the electromagnet 55 or 55 ' provided. The annular space between the pole piece 54 or 54 ' and the magnet 51 forms an axially exposed magnetic air gap to interact with the electromagnet, the gas having a non-magnetic and light filler 58 or 58 ' , such as foam or resin, filled with a non-magnetic low-friction shell 59 covered to form a smooth tread. The two end magnets 55 and 55 ' are also using nonmagnetic low friction sheath elements 56 and 56 ' covered.

The interior of the tube 52 is through a separator 53 divided into the two compression chambers II and II 'of the second stage. The inner surface of the tube 52 forms with the piston seals 33 and 33 ' the two in 2 shown short shafts 30 and 30 ' a gas-tight fit. Several flow communication channels 80 and 80 ' are between the inner surface of the tube 52 and the outer surfaces of the pole pieces 54 . 54 ' and the middle magnet 51 formed so that the fluid in the compression chamber I or I 'the first stage in a final magnet 55 or 55 ' and then into the inlet opening 81 or 81 ' of the canal 80 or 80 ' flow and out of the outlet openings 82 or 82 ' in the compression chamber II or II 'of the second stage can flow out. Because several channels 80 and 80 ' evenly along the circumference of the tube 52 are cut (only one is shown), have the outlet openings 82 or 82 ' gas bearing effect on the piston seal 33 or 33 ' ,

Within each end magnet 55 or 55 ' there is a non-magnetic socket 57 or 57 ' at each end of the tube 52 to support the suspension spring 61 or 61 ' represented in 2 , sits and also the tube magnetically separates from the spring. Are the jack 57 and the shaft 30 joined together, so forms a narrow gap between the two, which the fluid in space I entry into the inlet openings 81 of the channels 80 allowed.

Process of Float

With a new reference to 1A and 1B If the rotor is in a neutral position, ie if no current is fed into the two electromagnets, the position of the rotor will be determined by the biasing forces of the two suspension springs 61 and 61 ' certainly. In this position, there is each of the pole pieces 54 and 54 ' the rotor between the inner and the outer pole piece of the corresponding electromagnet, ie in its axially exposed magnetic air gap. Similarly, each outer pole piece is located 42 or 42 ' of the electromagnet between the middle magnet and one of the pole pieces 54 or 54 ' , ie in the axially exposed magnetic air gap of the rotor. In this application, the term "axially exposed magnetic air gap" is used to describe a magnetic air gap structure in which the two pole shoes defining a gap are positioned so that they have an axial distance such that the magnetic flux across the gap is generally in axial direction. Since both the electromagnets and the rotor have axially exposed magnetic air gaps, their respective pole pieces can be positioned in a mutually interposed relationship. Such interconnected relationships allow the runner a relatively long stroke without weakening the effective magnetic coupling between the rotor and the electromagnet, thus making the operation extremely efficient.

In 1B the electromagnets are energized, and the polarity of their two pole shoes is indicated by the lower case letters n and s, showing the interaction between the electromagnet and the rotor. The runner is moved to the left by the magnetic forces. In particular, there is the electromagnet 40 in a state in which his outer pole piece 42 n is and the inner s is such that its effect is the middle magnet of the runner 51 push away and the end magnet 55 to pull in the gap. On the other hand, there is the electromagnet 40 ' in a state where the other end magnet 55 ' is pushed away and the middle magnet 51 pulled in the direction of the gap. That means that the final magnet 55 with the electromagnet 40 and the middle magnet 51 with the electromagnet 40 ' forms a closed magnetic circuit. If the current passing through the two electromagnets is reversed, the rotor is moved in a similar manner to the other end. Since each solenoid always cooperates with at least one of the rotor magnets, its energy efficiency is high.

In 1B when the final magnet 55 ' to the steaming magnet 62 ' approaching, creating a strong repulsive force between the two. This strong damping force provides, together with the effect of the suspension spring 61 ' , which is compressed to almost its block length, and the gas spring formed by the space G ', which has been reduced to a small "dead" space, provides adequate protection to bump the runner onto the pole piece 44 ' to prevent. The three components of the suspension mechanism, ie the damping magnets which cooperate with the rotor end magnets as magnetic springs, the mechanical springs and the gas springs, are chosen so that the natural frequency of the rotor is approximately equal to that of the power source, ie 50 Hz or 60 Hz. corresponds so that the runner can work with his resonant frequency.

During operation, the rotor is precisely aligned by the piston heads and is held coaxial with the other parts of the compressor. Since the total contact area between rotor and piston heads is very small, friction and wear are low. On the other hand, since the pole faces of the electromagnets are generally of annular or cylindrical shape matching that of the rotor, they do not generate sideways drive forces during the reciprocation of the rotor. The only possible source of lateral force is the coil springs 61 and 61 ' but their sideways effects are due to the shafts 30 and 30 ' limited. All these components ensure a very small frictional resistance against the movements of the runner, and the runner can work without lubricants.

multistage compression

The compressor 10 is a double-acting machine because its rotor movements produce the same compression effects in two opposite directions. As for the path traveled by a process fluid, there are two gas communication / compression paths that are separated from each other. One starts at the right end at the gas inlet openings 71 on the base 41 , passes over the channels 70 into the pre-compression space I, and as the runner moves back, the gas flows into the end magnet 55 and then over the canal 80 into the compression chamber II 'of the second stage, and ultimately, on the next stroke of the rotor, the gas leaves through the short shaft 30 ' at the left end the compressor. The other path is formed in the same way in the opposite direction. In each gas flow path is through the sealing surface 56 a first one-way valve is formed, which the outlet openings 72 of the channels 70 opens and closes and a second one-way valve is removed from the sealing surface 33 ' the piston is formed, which the outlet openings 82 ' of the channels 80 opens and closes. Whether the channels 70 and 80 are open or closed, thus depends on the axial position of the rotor 50 from.

In 1A the runner is positioned so that he has all the channels 70 . 70 ' . 80 . 80 ' blocked, which can lead to no gas flow into the compressor or between the spaces in the compressor. In 1B the runner moves 50 to the left, the space in the right room I is enlarged and the channel 70 is open, so that gas is sucked in; at the same time is the channel 80 blocked and the space in the chamber II 'is reduced to zero, so that the gas therein through the exhaust valve 34 ' in the piston 32 ' is pushed out. On the other hand, the same rotor movement blocks the left channel 70 ' and the space in room I 'is reduced to the minimum, so that the gas contained therein only through the channels 80 ' in the room II of the next stage, which is expanded to suck in the gas. If the runner on the next stroke moved to the right, the process runs in the reverse direction.

In addition to the advantage of achieving multi-stage compression by a single moving part, the arrangement has the advantage that each compression operation has only a minimum of leakage through leakage. For example, when the runner moves to the left, both left spaces I 'and II' are in the compression phase, so that their internal pressure increases at the same time, and a leakage of space I toward space II is reduced. Similarly, the pressure in the gas spring space G 'is also high, which contributes to the reduction of the loss from the space I'. In addition, although there is a very narrow gap between the outer tread of the runner 59 and the inner tread of the lining element 25 In order to keep them practically non-contacting, this gap forms a long leakage path compared to the outer diameter of the rotor, so that when moving the rotor back and forth at high speed, any loss through this long gap is negligible. All these features make the lubricant-free operation practical, since the runner does not need any lubricant for sealing. Finally, it should be mentioned that due to the circumferential arrangement of the gas inlet openings in each room around around the corresponding running surfaces around this also cause gas-bearing effects that contribute to the reduction of friction and wear.

General Structure of the second embodiment

In the 4A and 4B are the general structure of the compressor 100 and its operation is very similar to those of the first embodiment. The main differences are in the central guide structure, the suspension mechanism, the multi-stage compression and the intercooler. Only these features will be described below.

In 5 has the central management system 130 over two end sections 131 and 131 ' each of which is fixed to a base of an electromagnet and a central portion 132 which is fitted between the end sections. Each end section has a low-friction cover 133 or 133 ' covered, which provides a Gleitdichtfläche. Two jacks 134 and 134 ' are at the two ends of the middle section 132 attached to support the suspension springs. A through hole is along the axis of the central guide 130 formed, which can be used for circulating a fluid for the purpose of cooling the compressor from the inside.

In 6 the runner has 150 over an inner pole piece 152 with an inner rib 153 holding the two gaskets 157 and 157 ' wearing. The seals also serve as sockets for suspension springs. The other parts of the rotor, ie its middle magnet, the two end magnets and the two Zwischenpolschuhe 154 and 154 ' are similar to those of the first embodiment.

As in 4A The two end magnets of the rotor are shown 150 if this in the compressor 100 is fitted, a sliding fit on the two end sections of the central guide, and the two seals 157 and 157 ' have a sliding fit on the central portion of the central guide, which ensures that during operation the runner is exactly coaxial with the other parts. The seals also divide the interior of the rotor into two gas-tight spaces, each containing a suspension spring 161 or 161 ' is fitted so that the runner is suspended during operation both by the action of the coil springs and the gas springs.

The annular space between each of the pole pieces 154 or 154 ' the rotor and the inner pole piece of a corresponding electromagnet forms a compression space I or I 'of the first stage. Two compression chambers of the second stage are formed by the annular spaces II and II 'between the end magnets of the rotor and their corresponding damping magnets. In the compression chambers I and I 'of the first stage are elastomeric rings 147 attached to the pole face of the inner pole piece, which ring serves to dampen a direct impact of the rotor on the pole piece and at the same time to avoid any dead space in the compression space. Similar rings 167 and 167 ' can be found in the compression chambers II and II 'of the second stage. An intermediate cooling space C is formed between the electromagnets, this space having communication passages for receiving compressed gas from the two compression spaces I and I 'of the first stage and for supplying the gas to the compression spaces II and II' of the second stage. All of these passages are around the perimeter of the lining element 125 formed around.

The gas communication paths in the compressor 100 be detailed with reference to 5 described in which the hatching patterns of different parts are omitted and the gas passages are shaded to make the image easy to read. A gas supply line passes through the housing wall to enter the space C and a coil 200 to build. The coil facilitates the heat exchange between the gas in the supply pipe and the outside thereof, so as to produce a cooling effect in the space C.

During operation, the gas in the pipe 200 With the channels 170 ' supplied, the outlet openings 172 ' in the compression space I 'of the first stage into this space. The same gas then gets out of the room through the channels through the rotor movement 180 ' over the one-way valves 182 ' pushed into the space C, so that the pressure in the room C increases. At the same time, the high-pressure gas in room C enters the channels 190 having outlet openings in the second stage chamber II at the other end. If the runner reverses his direction, the gas in room II will be exhausted 193 in the channels 195 forced out. Another parallel gas flow path is arranged in the same way in the opposite direction.

It It should be noted that the intermediate refrigerator C compressed gas from both rooms I and I 'the first Stage and receives the same gas two rooms II and II 'of the second stage supplies, whereby the operating conditions are the same on both sides. This carries to stabilize the double-acting work in opposite directions of the runner at. In such an arrangement, though there is only one moving component in the supercharger gives, in extremely efficient way high discharge pressure and a high flow rate achieved.

General Structure of the third embodiment

Now, the third embodiment of the invention will be described with reference to a compressor 300 represented in 7 to 9 , described. Numerous aspects of the compressor 300 and its basic operating principle is similar to those of the previous embodiments. New features include a three-coil motor stator, another rotor structure, a changed center guide, an improved magnet spring assembly, and other multi-stage compression and inter-cooling devices. These new features will be described in detail below.

As in 7 The compressor is shown 300 a linear motor formed by a stator 310 and a magnetic rotor 350 and a pair of compression devices 330 and 330 ' the second stage, each of which is attached to one end of the stator. In the interior of each compression device 330 or 330 ' is a piston 370 or 370 ' with the runner 350 connected and driven by this. In operation, a process gas enters the first-stage compression chambers inside the stator, then flows into the off-stator intercoolers to release some of the heat before entering the second-stage compression chambers in the devices 330 and 330 ' occurs and is further compressed there, which are located away from the engine, so that heat generated by the second compression stage, can be easily dissipated. Details of the static parts of the stator 310 and the facilities 330 and 330 ' are in 8th shown while the rotor element 350 and its connection to the two pistons 370 and 370 ' in 9 be illustrated.

In 8th has the stator 310 over a housing 311 made of a magnetic material that functions as part of the magnetic circuit of the stator. The housing 311 may have multiple outer ribs for strengthening mechanical strength and improving heat dissipation. A mechanically stable housing helps to keep all other static components precisely aligned, as will be described below. At each end of the case 311 is a basic element 312 or 312 ' attached, the one inner pole piece 313 or 313 ' wearing. Three winding spools 315 . 316 and 315 ' are axially inside the case 311 arranged and separated from each other by two annular pole pieces 314 and 314 ' separated. A non-magnetic cylinder 317 is fitted in the winding spools and between the inner pole shoes 313 and 313 ' trapped, creating a cylindrical interior for receiving the runner 350 is defined. Several through holes 324 and 324 ' are formed on the cylinder wall as a gas inlet into the spaces I and I '. In this arrangement, the four pole pieces form 313 . 314 . 314 ' and 313 ' between them, three axially exposed annular magnetic air gaps, each corresponding to a coil, so that when the coils are energized, a strong alternating flux is generated through the gaps for driving the reciprocations of the rotor. The presence of a third coil in the motor structure increases the total drive force on the rotor without changing the diameter and volume of the motor. Corresponding changes are made in the magnetic arrangement in the rotor as described below.

At the back of each pole piece 313 or 313 ' is a magnetic spring device comprising an inner magnet 319 or 319 ' , a rear pole piece 320 or 320 ' and an outside magnet 318 or 318 ' arranged. As indicated by the polarity of the magnets in 8th is shown, a strong flux concentration forms from the exposed surface of the magnet 319 or 319 ' to the inner edge of the pole piece 313 or 313 ' , which in principle represents the space of the compression space I or I '. In this arrangement, since the inner pole face of the magnetic spring is "nested" inside the outer magnet, most of the magnetic flux is "captured" within the spring structure, resulting in a more efficient and stronger spring. Furthermore, the outer magnet has 318 or 318 ' in comparison to the inner magnet 319 or 319 ' above a significantly larger volume, which allows the use of a low cost material, such as ferrite, in the spring assembly. Ferrite has the added advantage of not generating eddy current, and also has a higher maximum operating temperature.

Each of the compression devices 330 or 330 ' the second stage is at a corresponding base element 312 or 312 ' attached and includes a magnetic spring assembly. Since the two devices have an identical structure, only those on the right side, ie device 330 , described in detail. The device 330 has a generally cup-shaped housing 331 with outer ribs 332 made of a nonmagnetic and heat conductive material such as aluminum. The left side of the case 313 has a flange 333 on that to the shape of the case 311 fits so that the two can be precisely aligned and attached to each other. Inside the case 331 there is a cylinder element 340 the second stage, one end of which is on the pole piece 320 sits and the other end in the housing 331 Fits and with a cylinder head element 341 is closed. The cylinder 340 and the head element 341 define a second stage compression space II via gas inlet holes 343 through the cylinder wall and a gas outlet hole in the middle of the head element 341 features that through an exhaust valve 349 is covered. A seal 342 ensures the gas-tight fit of cylinder 340 and housing 331 , Another seal 345 is on the pole piece 320 attached to seal the piston skirt, this seal also supports the suspension spring, as will be described below. Between the cylinder 340 and housing 331 there is an annular space 346 , the compressed gas from the first stage compression via the exhaust valve 326 on the pole piece 320 absorbs and acts as an intermediate refrigerator.

In 9 the runner has 350 over a middle pole ring 351 , two middle magnets 352 and 352 ' , two intermediate pole shoes 353 and 353 ' and two end magnets 354 and 354 ' all at a central bolt 355 are made of non-magnetic material, which holds the magnets and the pole pieces coaxial. All from the runner 350 supported magnets are magnetized in the axial direction, so that each forms along its length an axially exposed magnetic air gap. Again due to the relatively large volume of the middle magnets 352 and 352 ' For example, the use of inexpensive material, such as ferrite, is possible to construct the rotor without losing magnetic force. The polarity of the magnets 352 . 352 ' . 354 and 354 ' is designed so that the same pole of the two middle magnets 352 and 352 ' in the direction of the common pole piece 351 so as to produce a concentrated radial magnetic flux. The outer surface of the middle magnet 352 or 352 ' is with a sealing element 356 or 356 ' covered to form a sliding seal with the inner surface of the cylinder 317 in 8th interacts. At each end of the central bolt 355 is a shaft 356 fitted, which serves as a central guide and extends through the base member of the stator and holds the rotor coaxial with the stator. Each shaft further carries a piston to perform the second stage of compression at the other end 370 or 370 ' that with a screw 371 or 371 ' is attached.

Again referring to 7 the runner gets off the pole pieces 320 and 320 ' carried by the two housings 331 and 331 ' are precisely aligned, and all other static components are aligned to ensure that the runner 350 and the two pistons 370 and 370 ' move back and forth practically without contact during operation. If the runner 350 in the central space in the interior of the stator 310 is fitted, it divides the space into two compression spaces I and I 'of the first stage. Similarly, the piston separates 370 or 370 ' the central space in each of the cylinders 340 or 340 ' the second stage in a compression chamber II or II 'the second stage and a spring chamber for receiving a suspension spring 348 or 348 ' , this space over the holes 344 or 344 ' in fluid communication with the intermediate refrigerator 346 or 346 ' stands. Since the spring chambers are constantly in fluid communication with the intermediate cooling chambers, they function as part of the entire intermediate cooling region.

The gas flow paths in the compressor 300 are in 7 represented by arrows. Moves the runner 350 to the right end, the volume of the first stage compression space I 'expands and gas is introduced through the gas flow passage formed by the inlet openings 321 ' on the stator housing 311 , the channels 322 ' on the inner pole piece and the openings 324 ' through the cylinder 317 , sucked. At the same time, the space II 'gas sucks the openings 343 ' from the intermediate refrigerator 346 ' one. If the runner reverses his movement, he blocks the openings 324 ' so that the gas in the room I 'compacted and through the channel 325 ' and the exhaust valve 326 ' in the intermediate refrigerator 346 ' is pressed while the gas in the room II 'compressed and through the exhaust valve 349 ' is urged.

Because cold gas entering the compressor 300 is made possible by the central part of the stator, a good cooling effect is generated on the coil and the rotor. On the other hand, the compressed gas coming from the room I or I 'will be temporary lig in the intermediate refrigerator 346 or 346 ' held and cooled there before it enters the room II or II ', making the process more efficient. In addition, the spaces II and II 'further away from the stator and the rotor, whereby the heat generated by the second stage of compression does not affect the operation of the engine and overheating of the engine is avoided.

10 shows a control circuit for the compressor 300 , An important concept presented in this circle is the generation of a phase difference between the winding coils 315 ' and 315 as the one group and the reel spool 316 than the other group, e.g. B. by connecting a capacitor C in parallel with the coil 316 , The the coils 315 ' and 315 flowing current I ₁ is the pointer sum of the coil 316 flowing current I ₂ and of the capacitor C flowing through current I ₃ , ie I 1 = I 2 + I 3 ,

Since the current through the capacitor C, ie the current I ₃ , compared to the current I ₂ through the coil 316 , which is practically an inductance element, leading, it follows that also the current I _{1 leads} the current I ₂ . Since the same current I ₁ the coils 315 ' and 315 flows through, this means that the magnetic driving forces of these two coils are always in phase with each other, but due to a phase difference, determined by the value of the capacitor C, that of the coil 316 generated driving force leads. During operation, as the rotor approaches the axial end position under the influence of the common driving forces of the three coils, the two end coils change 315 ' and 315 their current direction in time before the middle coil 316 whereby an effective bearing effect is generated, which enhances the effect of the suspension spring arrangement. Since this effect is achieved only when the runner is close to its end positions, this does not detract from the efficiency of the system, but overall increases efficiency through a better bearing rotor movement. By choosing an appropriate value for the capacitor C, fine tuning of the system for a particular application can be accomplished easily. The circuit also includes a protection thermistor R _t1 for starting surge prevention and an overheat protection circuit comprising a resistor R, a thermistor R _t2, and a relay switch S ₂ . The operation of the Schutzschaftkreises works in a conventional manner, which is why it needs no further description.

General Structure of the fourth embodiment

Now, the fourth embodiment of the invention will be described with reference to a compressor 500 , pictured in the 11 to 15 , described. Many aspects of the compressor 500 as well as its working principle are similar to those of the previous embodiments. New features include pole pieces of the solenoid having a flux switch and a pole face expansion structure, a circuit arrangement for generating phase differences in the drive coils, and a modified suspension assembly. These new features will be described in detail below.

In 11 includes the compressor 500 a stator 510 , a runner 550 , a pair of terminal equipment 530 and 530 ' and a central leadership that holds the entire unit together. In operation, process gas enters the rooms I and I 'through the stator and is then transferred from the runner to the intermediate refrigerators II and II' inside the terminals 530 and 530 ' and subsequently pressed into the spaces III and III 'to be further compressed and ultimately through the outlet valves in the valve blocks 540 and 540 ' to be urged.

In 12 became the central leadership 520 and the runner 550 removed to the details of the stator 510 and the terminal equipment 530 and 530 ' to show. The stator 510 has a housing 511 of a magnetic material that is part of the magnetic circuit of the stator. At each end of the case 511 is an end pole 512 or 512 ' appropriate. Three winding spools 515a . 515b and 515c are arranged coaxially inside the housing and separated from each other by two annular pole pieces 513 and 513 ' separated, the annular pole faces with toothed Polflächen-expansion structure 516 and 516 ' exhibit. The toothed structure ensures improved magnetic coupling between the rotor and the stator, especially when the current changes direction, by extending the pole face of the stator in the axial direction, and at the same time prevents excessive leakage of the fluid above it by maintaining a necessary gap length g between the tooth tips Split, as in 12 shown by the arrow. The pole shoes also have a magnet 514 and 514 ' formed flow switching device whose working principle with reference to the 14A to 14E is described.

A non-magnetic cylinder 517 is fitted inside the three coils and between the pole pieces 512 and 512 ' clamped and defines a cylindrical space for the runner 550 , Gas inlet openings 524 and 524 ' are on the cylinder 517 formed in a similar manner as in the preceding embodiment.

The device 530 has a non-magnetic housing 531 with outer ribs 523 made of a thermally conductive material, such as wise aluminum. The housing 531 has a flange 533 on, to the corresponding flange of the stator housing 511 fits to ensure a precise alignment between them. Inside the case 531 there is a cylinder 534 the second stage, one end of which is at the end pole 512 and the other end on the valve block 540 sitting. Around the cylinder 534 around is a magnetic spring formed of a winding spool 535 and a pole piece 518 , Between the magnetic spring and the housing 531 is an intermediate refrigerator II with corresponding inlet and outlet valve arrangements.

In 13 the runner has 550 over a middle pole ring 551 and two middle magnets 552 and 552 ' standing on a tubular element 555 made of non-magnetic material. At each end of the tubular element 555 is an intermediate pole piece 55 3 or 553 ' attached, the one end magnet 554 or 554 ' and a pole piece 556 or 556 ' holds. The magnet 554 or 554 ' and its end pole 556 or 556 ' are on a carrier element made of plastic or a composite carrier material 557 or 557 ' with an annular end portion having a piston surface 558 or 558 ' forms, attached. During operation, the piston face 558 or 558 ' In addition, a heat insulation ready to prevent overheating of the magnet. These magnets are all magnetized again in the axial direction, so that each forms along its length an axially exposed magnetic air gap between the corresponding pole shoes. That means the runner 550 has four magnetic air gaps to interact with the three formed in the stator magnetic air gaps. As described below, in each phase of operation always three magnetic air gaps on the rotor interact with the stator, while the other interacts with a magnetic spring.

The runner 550 is made of an inner suspension mechanism, formed of a central shaft 520 and a pair of mechanical springs 525 and 525 ' , carried. The central shaft 520 has a thicker middle section 522 with a middle flange 523 who carries the feathers. At each end of the middle section 522 there is a thin end section 521 or 521 ' passing through the support element 557 or 557 ' extends through. As in 11 is shown, the other end of the thin end portion extends 521 or 521 ' through the valve block 540 or 540 ' and the entire unit is precisely aligned and bolted. The shaft 520 is hollow, so that a coolant can be circulated around the entire unit, especially the runner 550 to keep refrigerated during operation.

The 14A to 14E show the operation principle of the flow switching mechanism used in the fourth embodiment. In 14A forms when the magnet 514 in an annular, in the pole piece 513 Made-in recess made by the magnet 514 The river created a closed circle through the narrow parts 513a and 513b to bring the flow in these parts almost to a river saturation level. 14B shows a similar, from a winding spool 514a generated flux distribution. Since these two alternatives work in a similar way, only those using the permanent magnet will work 514 described below.

14C shows the flux distribution when a rotor is fitted in a stator without current in one of the three coils. The one of the switching magnets 514 and 514 ' and that of the middle magnets 522 and 522 ' generated flux interact with each other to form two closed magnetic circuits which generate strong registration forces for holding the rotor at its neutral position where the magnetic resistance in each circuit is lowest. Will the stator, as in 14D shown, energized, is that of the magnets 514 and 552 generated flux with that of the coil 515a connected, the same applies to the magnets 514 ' and 522 ' with the coil 515b , whereby a combined driving force is generated in the direction of the right side, as shown by the large arrow below the drawing. Here it should be noted that most of the flow through each of the pole pieces 513 or 513 ' is switched to the left half of the extended Polflächenstruktur and no significant flow on the other side remains. Does the current reverse its direction, as in 14E shown, the flow through the switching magnet 514 and 514 ' to the other side of the pole shoes 513 and 513 ' switched, whereby the runner is driven in the opposite direction. By switching the flow from one half of the pole pieces to the other half in response to the change in the current direction, the magnetic coupling between the stator and the rotor is significantly improved, allowing the rotor a relatively long stroke with high energy efficiency.

15 shows a control circuit for the fourth embodiment. In this circle is every magnetic spring coil 535 or 535 ' with a capacitor connected in series, then the two with the coil 515a or 515c connected in parallel with the coil 515b is connected in series. Again, current I _{1 is} through the coil 515b the pointer sum of current I ₂ through the coil 515a and current I ₃ through the coil 535 or the pointer sum of current I ' ₂ through the coil 515c and current I ' ₃ through the coil 535 ' , ie, I 1 = I 2 + I 3 = I ' 2 + I ' 3 ,

In this way, the five coils are divided into three groups with different phase differences, the coils 535 and 535 ' the coil 515b leading, in turn, the coils 515a and 515c leads. In operation, when the runner has 550 approaching an end position, the magnetic spring coil 535 or 535 ' already changed their direction of current to produce a repulsive force from the coil 515b is supported in the middle to force the runner to move backwards. Again, fine tuning of the system can be achieved by choosing an appropriate value for the magnetic spring coils 535 and 535 ' and their corresponding capacitors are performed.

General Structure of the fifth embodiment

Now, the fifth embodiment of the invention will be described with reference to a compressor 600 , presented in the 16A to 20B , described. Numerous aspects of the compressor 600 and its basic operating principle is similar to those of the previous embodiments. New features include a more compact construction of the rotor assembly with a central guide extending the entire length thereof for the purpose of precisely aligning its components, a suspended stator construction to ensure the vibration free operation of the machine, which also has a cylinder extending through its entire length for purposes of precise alignment, includes a novel gas flow passage and check valves mounted inside the rotor's central guide. These novel features will be described in detail below.

In the 16A and 16B includes the compressor 600 a housing 610 formed by a tubular element 611 , and two terminals 620 and 620 ' one with a pair of cup springs 640 and 640 ' suspended stator 630 and a runner device 650 fitted in the stator with the two ends in each of the terminals 620 and 620 ' extend.

In 17 The stator and rotor assembly were removed to reveal the details of the housing 610 to show. The central portion of the housing is formed by the tubular element 611 formed, and the two ends are the terminal devices 620 and 620 ' by fastening means 619 attached to the middle section. The tubular element 611 has outer ribs 612 for improving mechanical strength and heat dissipation. The entire element is made of a magnetic material so that it acts as part of the magnetic circuit of the stator. Through holes 613 and 613 ' form the gas inlet into the housing. At each end of the element 611 there is a flange 614 or 614 ' for precise alignment with and for attachment to the terminal equipment 620 and 620 ' , The two terminal devices 620 and 620 ' are identical, so here only the decor 620 is described. The device 620 has a non-magnetic and heat-conducting body, shaped z. B. by aluminum casting. The casting has a cylindrical section 621 with outer ribs 622 for heat dissipation and a flange section 623 with a broad border 624 for engagement with the corresponding flange of the tubular element 611 , An elastomer element 625 is inside the rim 624 fitted and covers the inner surface of the flange portion 623 so that when the machine is assembled, a pair of cup springs 640 and 640 ' (not in 17 shown) between the elastomeric element 625 and an elastomeric bushing 615 be clamped to ensure a gas-tight fit. The elastomeric member has a surface which is shaped to conform to the end portion of the stator to provide disc spring and stator impact protection and heat and noise isolation as hereinafter described. Inside the cylindrical gate 621 there is a cylinder liner 626 that work together with a valve block 670 defines a compression space.

18 shows the structure of the stator 630 and its suspension springs 640 and 640 ' , The stator has a non-magnetic cylinder 631 which extends through its entire length and a cylindrical interior for receiving the central portion of the rotor device 650 Are defined. The cylinder 631 may be made of self-lubricating material, preferably of a composite material with metal or glass fiber reinforcement, due to mechanical strength and good thermal conductivity. The gas inlet channels and openings 634 and 634 ' are through the pole shoes and the cylinder 631 formed in a manner similar to the previous embodiments. Around the cylinder 631 There are four winding spools around 635a . 635b . 635c and 635d attached by three intermediate pole pieces 633a . 633b and 633c are separated from each other and from the two Endpolschuhen 633 and 633 ' held together. The intermediate pole shoes 633a . 633b and 633c have flux switching magnets as in the previous embodiment. Each end pole is equipped with a magnetic spring 636 or 636 ' attached to one end of the cylinder 631 is attached and also an attachment to the suspension spring 640 or 640 ' provides. Inside each magnet spring 636 or 636 ' is a plain bearing / sealing element 638 or 638 ' fitted to store the runner shaft. The disc springs 640 and 640 ' are from egg a thin laminate of thin metal plate (s) and non-metallic elastomeric plate (s) such as rubber or plastic, so that the springs also act as a membrane for partitioning the space between housings 610 and the stator 630 in separate gas-tight spaces, as will be described below, serve. The stiffness of the springs is chosen so that the natural frequency of the stator corresponds approximately to the frequency of the power supply.

In 19 the rotor device comprises a non-magnetic guide element in the form of a thin-walled tube 656 which carries all the other components and keeps them precisely aligned. The tube 656 can z. B. made of stainless steel or titanium. The middle section of the rotor is made up of a series of magnets and pole pieces comprising a central ring magnet 651 , two middle pole shoes 652 and 652 ' , two ferrules 653 and 653 ' and two end pole shoes 654 and 654 ' holding an elastomeric bush 655 and 655 ' as impact protection, formed. The central portion has a cylindrical outer surface coated with a self-lubricating film to form a sealing gap with the cylinder 631 in 18 , Inside the tube 656 There is a row of bar magnets 651a . 653 and 653a ' and pole shoes 652a . 652a ' . 654a and 654a ' , which fill the space inside the tube and form a very compact construction. Two reed valves 660 and 660 ' with inlet openings 657 and 657 ' and outlet openings 658 and 658 ' for disposable gas flow are also fitted inside the tube.

One each end of the tube 656 is with a piston head 665 or 665 ' via a universal joint formed by a spherical element 666 or 666 ' and a joint seat member 664 or 664 ' , connected. The use of a universal joint allows a "loose fit" between the rotor shaft and the piston head to ensure that the piston head 665 or 665 ' is exposed to non-sideward forces during operation, thereby minimizing wear of the seal surface. The piston head 665 or 665 ' can be made of self-lubricating plastic for lubrication-free operation. The use of a plastic piston has the advantage that the heat of compression is isolated and can not affect the magnets of the rotor. The seat element 664 or 664 ' of the joint is an extension of the valve 660 or 660 ' made of a lightweight and high strength material such as engineering plastics or carbon fiber materials. By inserting such an element into the thin-walled tube 656 the mechanical strength of the shaft is significantly increased. Assembled, the articulated seat member also retains a suspension spring as in the previous embodiment. The piston head also carries a one-way valve 667 or 667 ' , which allows the gas flow in the compression space.

The 20A and 20B show the structure of the reed valve 660 or 660 ' on. In 20A is the valve 660 from a valve seat 661 , a valve plate 662 and an outlet member 663 to which the valve is attached. The valve seat 661 and the outlet member 663 have corresponding angular surfaces with a narrow gap formed therebetween, in which the valve plate is located. The valve plate is made of a thin elastic plate, such as a stainless steel or beryllium copper plate. The valve plate is bent along the angular surface of the seat, so that it is caused by its own spring force to close the inlet opening. During operation, the angled surface on the outlet element serves 663 as a stop that prevents too much bending of the plate. 20B shows that the reed valve has a spring band 662a and a fastening tape 662b has, for the purpose of secure attachment a circle around the element 663 form. This construction ensures that a reliable tongue valve can be fitted into the limited space inside a runner shaft.

Now, referring to the 16A and 16B the operation of the compressor 600 described. If a compressor is assembled, then the stator is entirely through the two disc springs 640 and 640 ' suspended, and its outer cylindrical surface forms together with the inner surface of the tubular element 611 , which also serves as part of the magnetic circuit of the stator, a gap (in the 16A and 16B this gap is exaggerated for better illustration). This means that the stator itself has no physical contact with the housing 610 has and can swing freely. In operation, since both the stator and the rotor assembly are wholly suspended and able to move freely, and since the active and reactive forces between them are always equally strong and oppositely directed, the two cause each other to move in opposite directions Direction to balance each other's vibration effect. In this way, the machine as a whole has virtually no vibrations. The suspended stator also prevents noise transmission outside the compressor. Result is a quiet and vibration-free operation.

The compressor 600 is constructed double-acting with an internal multi-stage compression device. On each side of the compressor are four rooms, formed between the Ge housing 610 , the stator 630 and the runner establishment 650 , including a damper space I or I 'in the housing between the stator and disc spring, a first compression space II or II' inside the stator, a gap III or III 'between disc spring 640 or 640 ' and terminal equipment 620 or 620 ' and a last stage compression space IV or IV 'inside each terminal. As in 16B is shown, the rotor device 650 driven to the left, while the stator 630 is driven to the right by a reactive force. In this position, rooms II and IV on the right side draw gas from room I and III, respectively, while on the left side the gas in chamber II 'enters chamber III' via the reed valve 660 ' and the gas in room IV 'through the valve block 670 ' is pushed out. This means that in addition to the vibration-free operation, the movement of the stator, even if it is low, makes a positive contribution to the gas compression process.

At long last It is worth noting that, since the inlet gas in the damper spaces I and I 'is to, the Winding coils and the rotor magnets chilled and since the compression spaces IV and IV 'of the last stage spaced from the stator and positioned thermally isolated, the compression heat generated there the permanent magnet on the rotor not impaired, whereby the efficiency of the engine is high.

industrial applicability

• a) Hoher energetischer Wirkungsgrad, kompakte Struktur und niedrige Herstellungskosten.
• b) Hohe Druckleistung und Flussratenleistung.
• c) Schmiermittelfreier, ausleckungsfreier und instandhaltungsfreier Betrieb.
• d) Schwingungsfreier Betrieb mit geringer Geräuschentwicklung.
• e) Gute Wärmeabfuhr.
• f) Betriebssichere Aufhängung für eine lange, problemfreie Nutzungsdauer.

From the above description, it is easy to deduce that the linear motor and / or compressor according to the present invention has at least the following advantages.

• a) High energy efficiency, compact structure and low production costs.
• b) High pressure performance and flow rate performance.
• c) Lubrication-free, leak-free and maintenance-free operation.
• d) vibration-free operation with low noise.
• e) Good heat dissipation.
• f) Reliable suspension for a long, trouble free life.

ultimately is probably unnecessary to mention that the embodiments in this description have exemplary character and in a simple way adapted or modified by those skilled in the art can, if the basic concept of the invention has been understood. For example it is easy by combining the first two embodiments to achieve a three-stage compression within a unit while it is in the third and fourth embodiments possible is to put more coils in the stator and more magnets in the runner, to the engine more powerful and a relatively long, thin shape for better heat dissipation provide. Furthermore you can other impedance elements, such as the inductive or resistive type, for generating a phase difference be used between the winding spools.

Claims (20)

Linear motor ( 10 ; 100 ; 300 ; 500 ; 600 ) comprising: a stator ( 310 ; 510 ; 630 ); a reciprocating element ( 50 ; 150 ; 350 ; 650 ); and means for energizing the stator and / or the reciprocating member; characterized in that: the stator magnetic flux generating means ( 40 . 40 ' . 62 . 62 '; 315 . 315 ' . 316 . 318 . 318 ' . 319 . 319 '; 515a - 515c . 535 . 535 '; 635a - 635d ) which are arranged so that a plurality of axially exposed magnetic air gaps is formed; and the reciprocating member magnetic flux generating means ( 51 . 55 . 55 '; 352 . 352 ' . 354 . 345 '; 552 . 552 ' . 554 . 554 '; 651 . 653 . 653 ' ) formed to form a plurality of axially exposed magnetic air gaps to interact by thrust and pull forces with the magnetic air gaps of the stator. Linear Motor Compressor ( 10 ; 100 ; 300 ; 500 ; 600 ) comprising: a housing ( 20 ; 120 ; 311 ; 511 . 610 ), which has a stator ( 310 ; 510 ; 630 ) enclosing an interior defined; a reciprocating element ( 50 ; 150 ; 350 ; 550 ; 650 ), which is arranged in the interior; and means for energizing the stator and / or the reciprocating member; characterized in that it further comprises valve means ( 34 . 34 ' . 72 . 72 '; 82 . 82 '; 172 ' . 182 ' . 193 ; 326 . 326 ' . 349 . 349 '; 524 . 524 ' . 540 . 540 '; 660 . 660 ' . 667 . 667 ' . 670 . 670 ' ) to at least one fluid passage ( 70 . 70 ' . 80 . 80 '; 170 ' . 180 ' . 190 . 195 ; 322 ' . 325 ';) in and out of the interior; and wherein the stator magnetic flux generating means ( 40 . 40 ' . 62 . 62 '; 315 . 315 ' . 316 . 318 . 318 ' . 319 . 319 '; 515a - 515c . 535 . 535 '; 635a - 635d ) arranged to form a plurality of axially exposed magnetic air gaps; and the reciprocating member magnetic flux generating means ( 51 . 55 . 55 '; 352 . 352 ' . 354 . 345 '; 552 . 552 ' . 554 . 554 '; 651 . 653 . 653 ' ) arranged to form a plurality of axially exposed magnetic air gaps for interacting by thrust-and-pull forces with the magnetic air gaps of the stator. Device according to claim 1 or 2, wherein the magnetic air gaps of the stator ( 310 ; 510 ; 630 ) and the reciprocating member are arranged in an intermediate relationship. Device according to one of the preceding claims, wherein the magnetic flux generating means of the reciprocating member ( 50 ; 150 ; 350 ; 550 ; 650 ) made of permanent magnets ( 51 . 55 . 55 '; 352 . 352 ' . 354 . 345 '; 552 . 552 ' . 554 . 554 '; 651 . 653 . 653 ' ) and / or electromagnet is formed. Device according to one of the preceding claims, further comprising central guidance means ( 30 . 30 '; 130 ; 356 . 356 '; 520 ; 656 ) comprising the reciprocating element ( 50 ; 150 ; 350 ; 550 ; 650 ) coaxial with the stator ( 310 ; 510 ; 630 ) hold. Device according to claim 5, wherein the central guiding means ( 130 ; 520 ) is hollow to form a passage for circulating a cooling fluid. Device according to one of the preceding claims, further comprising a suspension mechanism for the reciprocating member ( 50 ; 150 ; 350 ; 550 ; 650 ), which has a magnetic spring arrangement ( 62 . 62 '; 318 . 318 ' . 319 . 319 '; 535 . 535 ' ). Apparatus according to claim 7, wherein the magnetic spring assembly comprises a nested permanent magnet and / or electromagnet structure ( 318 . 318 ' . 319 . 319 ' ) which forms a flux concentration therein. Device according to one of the preceding claims, further comprising elastomer elements ( 147 . 147 ' . 167 . 167 ' ) for damping the reciprocating element ( 150 ). Device according to one of the preceding claims, further comprising means ( 535 . 535 ' ) to produce a phase difference in the flow of the plurality of axially exposed magnetic air gaps of the stator and / or the reciprocating member. Apparatus according to claim 10, wherein said phase difference generating means ( 535 . 535 ' ) is an impedance element of the capacitive, inductive and / or resistive type. Apparatus according to claim 2 or any one of claims 3 to 11 in combination with claim 2, wherein the stator ( 310 ; 510 ; 630 ) and the reciprocating element ( 50 ; 150 . 350 ; 550 ; 650 ) are arranged to form at least one pre-compression space (I, I ') and another compression space (II, II'; III, III ', IV, IV'), and a one-way fluid passage is formed therebetween, so that a process fluid can be progressively compressed therein. Device according to claim 12, wherein the further compression space (II, II ';III;III'; IV, IV ') outside the stator ( 310 ; 510 ; 630 ) is formed. Apparatus according to claim 12 or 13, further comprising an intermediate cooling space ( 346 . 346 ' ), which is arranged between the Vorkompressionsraum (I, I ') and the further compression space (II, II'). Device according to one of the preceding claims, wherein the stator ( 510 ; 630 ) and / or the reciprocating element ( 550 ; 650 ) Polmittel ( 513 ) between two adjacent magnetic air gaps, wherein the pole means by magnetic means ( 514 . 514a ) in two axial sections ( 513a . 513b ) to form a mechanism for switching a flow from one of the axial sections to another in response to the change in the direction of an excitation current supplied to the stator and / or the reciprocating member. Apparatus according to claim 15, wherein the magnetic means ( 514 . 514a ) Permanent magnet means ( 514 ) which are magnetized in the axial direction, and / or electromagnetic means ( 514a ). Apparatus according to claim 15 or 16, wherein the pole means ( 513 ) further means ( 516 . 516 ' ) for expanding the pole face in the axial direction. Device according to one of the preceding claims, wherein both the stator ( 630 ) as well as the reciprocating element ( 650 ) are suspended so as to render them movable with respect to each other so that when in operation, the interaction between them will cause them to reciprocate in opposite directions. Device according to claim 18, wherein the stator ( 630 ) with disc spring means ( 640 . 640 ' ) is suspended to its precise alignment with the housing ( 610 ) to ensure. Device according to claim 19, wherein the disc spring means ( 640 . 640 ' ) also act as a membrane means, the space between the stator ( 630 ) and the housing ( 610 ) are divided into chambers so that the movement of the stator also produces compression effects.