LINEAR MOTOR COMPRESSOR

Abstract: A linear motor and/or compressor (10; 100; 300; 500; 600) comprises a housing (20; 120; 311; 511) fitted with a number of electromagnets (40, 40'; 140, 140'; 315, 315', 316; 515a-515c; 635a-635d), a shuttle (50; 150; 350; 550; 650) with a central guide (30, 30'; 130; 356, 356'; 520; 655) for keeping it coaxial with the electromagnets and a suspension mechanism for the shuttle including mechanical spring, gas spring and magnetic spring arrangements. The electromagnets form a number of axially exposed magnetic gaps to interact with axially exposed magnetic gaps formed on the shuttle to cause it reciprocate by push-and-pull forces. A phase difference can be produced between the electromagnets to improve shuttle suspension. The central guide can be made hollow to circulate a coolant to cool the compressor from inside. A multi-stage compression arrangement is formed between the shuttle and the electromagnets so that the compressor can work in a double-acting manner to compress the process fluid progressively for a high pressure output. A further suspension (640, 640') can be used for the stator (630) so as to ensure the machine's vibration-free operation.

Description: Linear Motor Compressor Technical Field of Invention This invention relates to a linear motor and a compressor incorporating such a motor Background of Invention The present invention provides improvements to tlie invention disclosed in my UK patent no GB-2299715-B, its disclosure is incorporated herewith by reference Summary of Invention A first object of this invention is to provide a linear motor and/or compressor with improved energy efficiency and more compact and cost effective structure According to one aspect of the invention, there is provided a linear motor comprising a stator having a magnetic arrangement defining a first plurality of axially exposed magnetic gaps, a reciprocating (shuttle) member, and means for energising tlie stator and/or reciprocating member, wherein the reciprocating member has a magnetic arrangement defining a second plurality of axially exposed magnetic gaps for interacting with the magnetic gaps of said stator According to another aspect of the invention, there is provided a linear motor compressor comprising a housing enclosing an inner space, a stator having a magnetic arrangement defining a first plurality of axially exposed magnetic gaps, a reciprocating member disposed as a free piston in the inner space, valve means for forming at least one fluid passage into and out of said inner space, and means for energising said stator and/or reciprocating member, wherein the reciprocating member has a magnetic arrangement defining a second plurality of axially exposed magnetic gaps for interacting with the magnetic gaps of said stator It is advantageous to arrange between the stator and the shuttle a senes of magnetic gaps along the shuttle's operating axis so that the diameters of the stator and shuttle can be made small It is also advantageous to arrange the stator and shuttle's magnetic gaps in an interposed relationship so that it improves not only the push-and-pull dnving forces but also electromagnetic suspension effects on tlie shuttle, therefore improving energy efficiency and reducing working load on suspension spπngs Preferably the stator windings are divided into two or more groups and a phase difference is introduced in their currents to further enhance suspension effects In case that a stronger dnving force is required by a particular application, it can be achieved conveniently by arranging more magnetic gaps along the stator and shuttle structure, forming a longer and more powerful unit Such a relatively thin and long configuration provides better heat dissipation which is highly beneficial to a high powered unit, especially when it uses temperature sensitive rare earth magnets It is preferable that the shuttle member is supported by a central guide to ensure its non- contact movements relative to the stator and to form a clearance seal allowing lubricant-free operation The central guide can be a hollow shaft extending through said reciprocating member to circulate a coolant fluid through it Alternatively, the central guide can be formed by a pair of coaxially aligned shafts with pistons earned by the reciprocating member It is also preferable to form a multi-stage compression arrangement by dividing the space inside the compressor into pre-compressing and further-compressing chambers so that a process fluid can be compressed stage by stage Advantageously, an intermediate chamber can be formed to receive compressed fluid from said pre-compressing chamber for lntercoohng then to supply it to said further-compressing chamber It is advantageous to arrange second stage compression chambers outside tlie linear motor structure to improve heat dissipation and energy efficiency A further object of this invention is to provide an improved suspension mechanism for a reciprocating member m a linear motor, therefore to make tlie motor operation more efficient and more reliable According to yet another aspect of the invention, there is provided a mechanism for suspending a reciprocating member in a linear motor, wherein said linear motor has a stator with pole means for interacting with pole means on said reciprocating member to cause the latter to reciprocate between two end positions, and wherein said suspension mechanism includes magnetic spnng means arranged to interact with the pole means of said reciprocating member so as to generate a return force in response to its movement towards each said end position Preferably, said magnetic spnng means have a nested permanent magnet structure forming internal flux concentration for acting with said reciprocating member when it enters the structure Alternatively, said magnetic spnng means is formed by an electromagnet with an axially exposed magnetic gap for acting with said reciprocating member A further object of this invention is to provide a linear motor with a flux switching arrangement for making the motor operation more efficient According to yet another aspect of the invention, there is provided a flux switching mechanism for a linear motor having a stator with pole means defining a plurality of magnetic gaps for interacting with pole means on a reciprocating member, wherein the pole means of said stator incorporate flux switching means for switching magnetic flux towards one axial direction according to the direction of an energising current supplied to the stator so as to improve magnetic linkage between the stator and the reciprocating member Preferably the stator pole means also have a pole face extension pattern extending in axial direction to further improve said magnetic linkage A further object of this invention is to provide a linear motor and/or compressor with a suspension mechanism for its vibration-free operation According to yet another aspect of tlie invention, there is provided a linear motor and/or compressor having a housing accommodating a stator and a reciprocating (shuttle) member, wherein both said stator and reciprocating member are suspended to make them movable relative to the housing so that when in operation the interaction between the stator and the reciprocating member would cause them to move in opposite direction Preferably the stator is suspended by disk spnng means which also ensures its precise alignment with the housing It is advantageous that the disk spnng means also act as diaphragm means dividing the space between the stator and tlie housing into chambers so that the stator's movement would also produce compression effects Brief Description of Drawings Further features, advantages and details of the invention are to be descnbed with reference to preferred embodiments illustrated in the accompanying drawings, in which Figs 1A and IB are cross-sectional views taken along the central axis of a compressor according to a first preferred embodiment of the present invention, Fig 2 is a sectional view showing static parts of the first embodiment, Fig 3 is a sectional view of a shuttle in the first embodiment, Figs 4A and 4B are sectional views taken along the central axis of a compressor according to a second preferred embodiment of the present invention, Fig 5 is a sectional view showing static parts of the second embodiment, Fig 6 is a sectional view of a shuttle in the second embodiment Fig 7 is a sectional view taken along the central axis of a compressor according to a third preferred embodiment of the present invention, Fig 8 is a sectional view showing static parts of the third embodiment, Fig 9 is a sectional view of a shuttle assembly in the third embodiment, Fig 10 shows a control circuit for the third embodiment, Fig 11 is a sectional view taken along the central axis of a compressor according to a fourth preferred embodiment of the present invention, Fig 12 is a sectional view showing static parts of the fourth embodiment, Fig 13 is a sectional view of a shuttle assembly in the fourth embodiment, Figs 14A to 14E illustrate working pnnciples of a flux switching mechanism, Fig 15 is a control circuit for the fourth embodiment of tlie present invention, Figs 16A and 16B are sectional views taken along the central axis of a compressor according to a fifth preferred embodiment of the present invention, Fig 17 is a sectional view of a housing structure of the fifth embodiment, Fig 18 is a sectional view of a stator in tlie fifth embodiment, Fig 19 is a sectional view of a shuttle assembly in the fifth embodiment, and Figs 20A and 20B illustrate the structure of a reed valve Detailed Description of Preferred Embodiments In this application, the invention is descnbed as a compressor for the sake of easy understanding It should be understood that the same concept can be used for gas as well as for liquid, and also for a vacuum pump Therefore, the tenn "compressor" should be interpreted as covenng all these applications, unless specifically stated otherwise Also, the same concept can be used to build a linear motor by simply removing valves and seal members For this reason, there is no need for a separate descnption on how to change each compressor embodiment into a linear motor Furthermore, the term "magnetic arrangement" used in this application should be interpreted to cover any arrangement for generating magnetic flux, including electromagnet, permanent magnet or a combination of both There is no need to mention that replacing one type of "magnetic arrangement" by the other or combining the both types together would be obvious once tlie working pnnciples are explained Finally it is also obvious that an efficient motor design can also be used as a electnc generator by operating it in a reverse manner, I e by using a mechanical input to dnve the motor which in turn produces an electnc output General Structure of the First Embodiment In Fig 1A, a compressor 10 has a housing 20, two annular electromagnets 40 and 40' secured to the two ends of the housing, two short shafts 30 and 30' (not in section), each fitted in the centre of one electromagnet, a shuttle member 50 earned by the short shafts, and a suspension mechanism including helical spnngs 61 and 61 ' and cushioning magnets 62 and 62' Tlie two electromagnets 40 and 40' are arranged in a similar way as in my UK patent no GB-2299715-B for generating a push-and-pull force onto the shuttle 50 The compressor 10 is a double-acting unit with an internal multi-stage compression arrangement, which includes three pairs of separated chambers formed between the shuttle 50 and the electromagnets 40 and 40' Specifically, two first-stage compressing chambers I and I' are the annular spaces between each axial end of tlie shuttle 50 and a cushioning magnet 62 or 62', into which tlie process fluid is supplied from outside tlie compressor via channels 70 and 70' Two second-stage compressing chambers are formed by the cy ndncal spaces II and II' inside tl e shuttle 50, into winch the process fluid is supplied from tlie chambers I and I' via channels 80 and 80' Two further chambers G and G' are the annular spaces around the shuttle pole pieces 54 and 54', forming gas spnngs as part of the shuttle's suspension mechanism In Fig 2, the housing 20 has a non-magnetic cyhndncal wall 21 with a number of outer fins 22 for better mechanical strength and thermal dissipation The two electromagnets are identical, therefore only the nght one 40 is descnbed here The corresponding parts of the left electromagnet 40' is indicated by the same reference numbers with an apostrophe ' The electromagnet 40 has a magnetic base member 41 secured by fastening means 23 to the housing 20 Its magnetic circuit is formed by an annular outer pole piece 42, which is connected to the base 41 via a magnetic member 43, and a coaxial inner pole piece 44, directly connected to the base at its rear end A toroidal coil 45 is fitted in the annular space defined by the members 42, 43, 41 and 44 An axially exposed magnetic gap is fonried between tlie pole pieces 42 and 44 for interacting with tlie shuttle's pole piece, as to be descnbed later Clamped between the two electromagnets is a separation nng 24 made of a non-magnetic and thermally conductive matenal, such as brass or aluminium, to improve the compressor's heat dissipation A non-magnetic lining member 25 is fitted inside the nng 24, extending into the magnetic gaps of the two electromagnets That is to say, the lining member 25 provides a complete and smooth inner surface for closely matching the outer surface of the shuttle 50, so that when the clearance between them is at the level of about lOμm, it would fomi a clearance seal preventing gas leakage through them The two end portions of the lining member 25 also define the outer wall of the gas spnng chambers G and G' The inner pole piece 44 has on its inner surface a lining member 46 forming the outer wall of the pre-compressing chamber I The two shafts 30 and 30' are axially aligned to guide the shuttle's movements They are identical so only one, I e the nght one 30, is descnbed here The shaft 30 has a tubular portion 31, a piston head 32 fitted to one end of the portion 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 made of a self-lubncating matenal, such as Teflon, for lubncant-free operation Shuttle Structure In Fig 3, the shuttle 50 has an annular shaped middle magnet 51 magnetised in radial direction, e g its outer penphery is the North (the outer pole) and the inner penphery the South (the inner pole) so that its outer surface produces radial magnetic flux evenly distπbuted over its whole circumference for acting with the annular poles of the electromagnets A magnetic tubular member 52 is fitted inside the annular magnet 51 , serving as its inner pole piece Two intermediate pole pieces 54 and 54' are each fitted to one end of the tube 52, and at their axial ends are two end magnets 55 and 55', which are magnetised in axial direction The polanty of the magnets are arranged in a way that the pole piece 54 or 54' is magnetically connected to the south pole of the middle magnet 51 and that of the end magnet 55 or 55', therefore it provides highly concentrated magnetic flux for acting with tlie electromagnet 40 or 40' The annular space between the pole piece 54 or 54' and the magnet 51 forms an axially exposed magnetic gap for interacting with the electromagnet, which gas is filled with a non-magnetic and light-weight filling stuff 58 or 58', such as foamed plastics or resin, and covered by a non-magnetic low-fnction sleeve 59 to form a smooth beanng surface The two end magnets 55 and 55' are also covered by non-magnetic low- friction sleeve members 56 and 56' The intenor of the tube 52 is divided by a separation member 53 into the two second-stage compressing chambers II and II' The inner surface of the tube 52 forms gas-tight fit with tlie piston seals 33 and 33' of the two short shafts 30 and 30' shown in Fig 2 A number of fluid communication channels 80 and 80' are formed between the outer surface of the tube 52 and the inner surfaces of the pole pieces 54, 54' and the middle magnet 51, so that the fluid in the first-stage compressing chamber I or Y can flow into an end magnet 55 or 55' then into the inlet hole 81 or 81 ' of the channel 80 or 80' and come out of the outlet hole 82 or 82' in the second-stage compressing chamber II' or π Since there are a number of channels 80 and 80' eva ly cut around the penphery of the tube 52 (only one of each is shown), the outlet holes 82 or 82' have gas beanng effects on the piston seal 33 or 33' Within each end magnet 55 or 55', there is a non-magnetic bushing 57 or 57' sitting against each end of the tube 52 for supporting the suspension spnng 61 or 61 ' shown in Fig 1 A, and also magnetically separating the tube from the spnng When assembled, a small gap is formed between the bushing 57 and the shaft 30, allowing the fluid in the chamber I to enter the inlet holes 81 of the channels 80 Reciprocating Operation Now return to Figs 1A and IB In Fig 1A, tlie shuttle 50 is at a neutral position, l e when there is no current in the two electromagnets the shuttle position is decided by the biasing forces of the two suspension spnngs 61 and 61' At this position each of the shuttle's pole pieces 54 and 54' is interposed between the inner and outer pole pieces of the corresponding electromagnet, I e in its axially exposed magnetic gap Similarly, each of the electromagnet's outer pole piece 42 or 42' is interposed between the middle magnet and one of the pole piece 54 or 54', l e in the shuttle's axially exposed magnetic gap In this application, the term "axially exposed magnetic gap" is used to descnbe a magnetic gap structure in which the two pole pieces defining a gap are positioned to have an axial distance so that tlie magnetic flux over the gap would be generally in axial direction Since both the electromagnets and the shuttle have axially exposed magnetic gaps, their respective pole pieces can be positioned in a mutually interposed relationship Such a mutually interposed relationship allows the shuttle a relatively long stroke without weakening the effective magnetic linkage between the shuttle and the electromagnets, therefore making the operation highly efficient In Fig IB, the electromagnets are energised and tlie polanty of their pole pieces is marked by low case letters n and s, showing the interaction between the electromagnets and the shuttle The shuttle is dnven by the magnetic forces to the left More particularly, the electromagnet 40 is at a status that its outer pole piece 42 is n and the inner one 44 is s, so its effect is to push tlie shuttle's middle magnet 51 away and to pull the end magnet 55 into the gap On the other hand, the electromagnet 40' is at a status to push the other end magnet 55' away and to pull the middle magnet 51 towards the gap That is to say, the end magnet 55 forms a closed magnetic circuit with the electromagnet 40 and the middle magnet 51 with the electromagnet 40' When the current passing through tlie two electromagnets is reversed, the shuttle will be dnven to the other end in a similar way Because each electromagnet would always act with at least one of the shuttle magnets, its energy efficiency is high In Fig IB, as the end magnet 55' approaches the cushioning magnet 62', a strong repelling force is generated between them This strong cushioning force together with the effects of the suspension spnng 61 ', which is compressed close to its solid length, and the gas spnng formed by the chamber G', which is reduced to a small "dead" space, provide adequate protection to prevent the shuttle from hitting the pole piece 44' The three elements of the suspension mechanism, I e tlie cushion magnets, which act with the shuttle's end magnets as magnet spnngs, mechanical spnngs and gas spnngs, are selected to make the shuttle's natural frequency close to that of the power supply, e g 50Hz or 60Hz, so that the shuttle can operate at its resonant frequency Duπng operation, the shuttle is precisely aligned by the piston heads and kept coaxial with the otlier parts of the compressor Because the total contacting area between the shuttle and the piston heads is very small, fnction and wear are also small On tlie other hand, since the electromagnets' pole faces are generally annular or cyhndncal in shape, matching that of the shuttle's, they produce no sideways dnving forces dunng tlie shuttle's reciprocating movements The only possible source of side force is the helical spnngs 61 and 61 ', but their sideways effects are restncted by the shafts 30 and 30' All these elements ensure that the total fnction resistance to the shuttle's movements is very small and the shuttle can operate lubncant-free Multi-stage Compression The compressor 10 is a double-acting machine for its shuttle movements in two opposite directions produce the same compressing effects When considenng the path travelled by a process fluid, there are two gas communication/compression routes, which are mutually separated One starts from the nght end at the gas inlet holes 71 on the base 41 , goes into the pre-compressing chamber I via the channels 70, then as tlie shuttle moves back, the gas flows into tlie end magnet 55 and then via the channel 80 into the second-stage compressing chamber II', and finally at the next shuttle stroke tlie gas leaves the compressor through the short shaft 30' at tlie left end Tlie other route is formed in the same way in opposite direction In each gas flow route, a first one-way valve is formed by the shuttle's sealing surface 56 which opens and closes tlie outlet holes 72 of tlie channels 70 and a second one-way valve is formed by the piston's sealing surface 33' which opens and closes tlie outlet holes 82' of the channels 80 That is to say, whether tlie channels 70 and 80 are opened or closed depend on the axial position of the shuttle 50 In Fig 1 A, the shuttle is positioned to block all the channels 70, 70' 80 and 80' so there is no gas flow into the compressor or between the chambers inside the compressor In Fig IB, the shuttle 50 moves to the left, the space in the nght chamber I is expanded and the channels 70 is opened so gas is sucked in, at tlie same time the channels 80 is blocked and tlie space in the chamber II' is reduced to zero so the gas in it is forced out through the outlet valve 34' in the piston 32' On the otlier hand, the same shuttle movement blocks the left channels 70' and the space in the chamber Y is reduced to mimmum so the gas in it can only go via the channels 80' into the next stage chamber II which is expanded to suck the gas in In next stroke when the shuttle moves to nght the process reverses direction In addition to the advantage of achieving two-stage compression by a single moving part, the arrangement also has tlie advantage that each compressing operation has minimum leakage For example, when the shuttle moves to the left, the left chambers I' and D' are both at their compressing phase so their internal pressure increases at die same time, and the leakage from the chamber II' into the chamber I' is reduced Similarly, the pressure in the gas spnng chamber G' is also high, which helps to reduce the leakage from the chamber I' Further, although there is a very small gap between the shuttle's outer beanng surface 59 and the inner beanng surface of the lining member 25 for keeping them virtually non-contact, this gap forms a long leakage route compared with the shuttle's outer diameter so when the shuttle reciprocates at high speed any leakage through this long gap would be ignorable All these features make the lubncant-free operation practical because the shuttle does not rely on lubncant for sealing Finally, it is worth mentioning that because the gas inlet holes into each chamber are arranged penpherally around the corresponding beanng surfaces, they also produce gas beanng effects which help to reduce fnction and wear General Structure of the Second Embodiment In Figs 4 A and 4B, the general structure of a compressor 100 and its operation are similar to that of the first embodiment The main differences are in its central guide structure, suspension mechanism, multi-stage compression and lntercoohng arrangement Only these new features are descnbed below In Fig 5, a central guide 130 has two end sections 131 and 131 ', each secured to a base of an electromagnet, and a middle section 132 fitted between the end sections Each end section is covered by a low-fnction sleeve 133 or 133' which provides a sliding seal surface Two bushings 134 and 134' are fitted at tlie two ends of tlie middle section 132 for supporting suspension spnngs A through hole is formed along the axis of the central guide 130, which can be used to circulate a fluid to cool the compressor from within hi Fig 6, the shuttle 150 has an inner pole piece 152 with an internal ndge 153 which bears two seal nngs 157 and 157' The seals also serve as bushings for suspension spπngs The shuttle's other parts, l e its middle magnet, two end magnets and two intennediate pole pieces 154 and 154' are similar to that of the first embodiment As shown in Fig 4A, when the shuttle 150 is assembled in the compressor 100, its two end magnets have sliding fit on the two end sections of the central guide and the two seals 157 and 157' have sliding fit on the middle section of the central guide, which ensure tlie shuttle is precisely coaxial with the other parts dunng operation Tlie seals also divide the shuttle's internal space into two gas- tight chambers, in each of which is fitted a suspension spnng 161 or 161 ' so that in operation the shuttle is suspended by the effects of both the helical spπngs and the gas spπngs The annular space between each of the shuttle's pole piece 154 or 154' and die inner pole piece of a corresponding electromagnet forms a first-stage compressing chamber I or Y Two second- stage compressing chambers are formed by the annular spaces II and II' between tlie shuttle's end magnets and their corresponding cushioning magnets In the first-stage compressing chambers I and F there are elastomenc nngs 147 fitted on the pole face of tlie inner pole piece, which nng is to cushion the shuttle from hitting the pole piece directly and at the same time avoid any dead space in the compressing chamber There are similar nngs 167 and 167' in the second-stage chambers II and II' An interceding chamber C is formed between t e two electromagnets, which chamber has gas communication passages for receiving compressed gas from die two first-stage compressing chambers I and I' and for supplying the gas to the two second-stage compressing chambers II and ET All these passages are formed around the penphery of the lining member 125 The gas communication routes in the compressor 100 are descnbed in detail wrth reference to Fig 5, in which the hatching patterns of different parts are deleted and the gas passages to be descnbed are shaded so as to make the illustration easy to read A gas inlet line passes through the housing wall to enter the chamber C and form a coil 200 The coil helps heat exchange between the gas in the inlet tube and that outside it to produce cooling effects in the chamber C In operation, the gas in the tube 200 is supplied via channels 170', which have outlet holes 172' in the first-stage compressing chamber I', into diat chamber Then the same gas is forced by the shuttle movement out of die chamber through channels 180' and into the chamber C via the one-way valves 182', so the pressure in the chamber C builds up At the same time, the high pressure gas in the chamber C enters channels 1 0 which have outlet holes in the second-stage chamber II at the other end When the shuttle reverses its movement, die gas in the chamber II is forced out via the outlet valves 1 3 in channels 195 Another parallel gas flow route is arranged in the same way in opposite direction It should be noted that the lntercoohng chamber C receives compressed gas from both first- stage chambers I and I', and supplies the same gas to bodi second-stage chambers II and II', so the operating conditions at both sides are the same This helps to stabilise the shuttle's double acting operation in opposite directions In such an arrangement, although there is only one moving part inside the compressor, it achieves high output pressure and flow rate in a very efficient manner General Structure of the Third Embodiment Now the third embodiment of this invention is descnbed witii reference to a compressor 300 shown in Figs 7 to 9 Many aspects of the compressor 300 and its basic working pnnciples are similar to that of the earlier embodiments New features include a three-coil motor statoi, a different shuttle structure, a revised central guide arrangement, an improved magnet spnng arrangement and different multi-stage compression and lntercoohng arrangements The new features are descnbed below in details As shown in Fig 7, the compressor 300 includes a linear motor formed by a stator 310 and a magnetic shuttle 350, and a pair of second stage compression assemblies 330 and 330', each fitted to one end of the stator Inside each compression assembly 330 or 330', a piston 370 or 370' is connected to and dnven by the shuttle 350 In operation, a process gas first enters first stage compression chambers inside the stator, then it flows into lntercoohng chambers located outside the stator to release some of the heat before entenng and being further compressed in second stage compression chambers in the assemblies 330 and 330', which are located away for the motor so that heat generated by second stage compression can be easily dissipated Details of die static parts of die stator 310 and the assemblies 330 and 330' are shown in Fig 8 while that of the shuttle member 350 and its connection with the two pistons 370 and 370' in Fig 9 In Fig 8, the stator 310 has a housing 311 made of magnetic matenal serving as part of the stator magnetic circuit The housing 311 can have a number of outer fins to increase its mechanical strengύ and to improve heat dissipation A mechanically strong housing also helps to keep all the other static parts precisely aligned, as to be further descnbed below At each end of the housing 311 is fitted a base member 312 or 312' which carnes an inner pole pieces 313 or 313' Three winding coils 315, 316 and 315 'are axially arranged inside the housing 31 1 and separated from one another by two annular pole pieces 314 and 314' A non-magnetic cylinder 317 is fitted inside die winding coils and clamped between the two inner pole pieces 313 and 313', defining a cyhndncal inner space for accommodating the shuttle 350 A number of throughholes 324 and 324' are formed on the cylinder wall as gas inlet to the chambers I and Y In this arrangement, the four pole pieces 313, 314, 314' and 313' form between them three axially exposed annular magnetic gaps, each corresponds to a coil so that when die coils are energised strong alternating flux would be generated across d e gaps to dnve the shuttle's reciprocation movements By having a third coil in the motor structure, total dnving force on the shuttle is increased witiiout changing motor diameter and volume Corresponding changes are made in magnetic arrangement in the shuttle, as to be descnbed below At die back side of each inner pole piece 313 or 313', there is arranged a magnet spnng assembly including inner magnet 319 or 319', back pole piece 320 or 320' and outer magnet 318 or 318' As shown by die polanty of the magnets in Fig 8, a high flux concentration is formed from die exposed face of die magnet 319 or 319' to the inner edge of the pole piece 313 or 313 ' which is basically the space of the compression chamber I or I' In this arrangement, because the inner pole face of the magnet spnng is "nested" inside the outer magnet, most of the magnetic flux is "trapped" inside spnng structure which makes the spnng more effective and powerful Further, since the outer magnet 318 or 318' has a much larger volume compared with the inner magnet 319 or 319', it allows the use of low cost matenal, such as fernte, in the spnng assembly Fernte has the extra advantages of generating no eddy currents and also has a higher maximum working temperature Each of die second stage compression assembly 330 or 330' is fitted against an associated base member 312 or 312', enclosing a magnet spnng arrangement Since the two assemblies are identical in structure, only the one at the nght-hand side, l e the assembly 330 is to be descnbed in detail Tlie assembly 330 has a generally cup-shaped casing 331 with external fins 332 made of a non-magnetic and thermally conductive matenal, such as aluminium The left-hand side of the casing 331 has a flange 333 which matches the shape of die housing 311so diat the two of them can be precisely aligned and secured together Inside die casing 331 is a second stage cylinder member 340 with one end sitting against the pole piece 320 and die odier end fitting into die casing 331, closed by a cylinder head member 341 The cylinder 340 and die head member 341 define a second stage compression chamber π, which has gas inlet holes 343 through the cylinder wall and a gas outlet hole in the middle of the head member 341, which is covered by an outlet valve 349 A seal 342 ensures gas-tight fit between the cylinder 340 and die casing 331 Another seal 345 is fitted on die pole piece 320 to seal a piston shaft, which seal also supports a suspension spnng as to be descnbed later Between the cylinder 340 and the casing 331, there is an annular space 346 which receives compressed gas from the first stage compression via the outlet valve 326 on the pole piece 320 and works as an lntercoohng chamber In Fig 9, the shuttle 350 has a middle pole nng 351, two middle magnets 352 and 352', two intermediate pole pieces 353 and 353' and two end magnets 354 and 354', all fitted on a central pin 355 made of non-magnetic matenal, which keeps the magnets and pole pieces coaxial All die magnets earned by the shuttle 350 are magnetised in axial direction, so each of them forms an axially exposed magnetic gap along its length Again, due to die relatively large volume of the middle magnets 352 and 352', it is possible to use low cost matenal, such as fernte, to build die shuttle wrthout sacπficing its magnetic strength The polanty of the magnets 352, 352', 354 and 354' are arranged in a way tiiat the two middle magnets 352 and 352' have die same pole towards die common pole piece 351 so as to generate concentrated magnetic radial flux The outer surface of the middle magnet 352 or 352' is covered by a seal member 356 or 356' to form a sliding seal working with die inner surface of die cylinder 317 Fig 8 At each end of die central pin 355 is fitted a shaft 356 or 356', which serves as a central guide to extend through the stator's base member and keep die shuttle coaxial with die stator Each shaft also carnes at the odier end a piston 370 or 370' fastaied by a screw 371 or 371 ' for performing second stage compression Now back to Fig 7, the shuttle is supported by die pole pieces 320 and 320', winch are precisely aligned by the two casings 331 and 331 ', and all die otiier static members are aligned to ensure tiiat the shuttle 350 and die two pistons 370 and 370' can have virtually non-contact reciprocating movement in operation When the shuttle 350 is fitted into die central space inside die stator 310, it divides the space into two first stage compression chambers I and I' Similarly, die piston 370 or 370' divides die central space in each of the second stage cylinder 340 or 340' into a second stage compression chamber II or II' and a spnng chamber for accommodating a suspension spnng 348 or 348', which chamber is in fluid communication witii die lntercoohng chamber 346 or 346' via the holes 344 or 344' Since the spnng chambers are always in fluid communication wrth die lntercoohng chambers, they work as part of the total lntercoohng space The gas flow routes in the compressor 300 are shown by the arrow signs in Fig 7 When the shuttle 350 moves to die nght-hand end, the volume of the first stage compression chamber Y expands and gas is sucked in ti rough a gas flow passage formed by die inlet holes 321 ' on die stator housing 311, the channels 322' on the inner pole piece and holes 324' through the cylinder 317 At the same time, die chamber II' sucks in gas from the lntercoohng chamber 346' via the holes 343' When die shuttle reverses its movement, it will block the holes 324' so the gas in die chamber I' will be compressed and forced through the channel 325' and die outlet valve 326' into die lntercoohng chamber 346', while the gas in the chamber II' will be compressed and forced out through the outlet valve 349' By allowing cold gas to enter the compressor 300 through the middle part of the stator it produces good cooling effects to the coils and the shuttle On die odier hand, die compressed gas coming out of the chamber I or I' is temporanly stored in the lntercoohng chamber 346 or 346' where it is cooled before entenng the chamber II or II', making die whole process more efficient Further, because die chambers II and II' are further away from the stator and shuttle, the heat generated by second stage compression would not affect the motor operation, avoiding motor overheating Fig 10 shows a control circuit for the compressor 300 An important concept shown in this circuit is that a phase difference is produced between die winding coils 315' and 315 as one group and the winding coil 316 as anotiier group e g by connecting a capacitor C in parallel with the coil 316 The current Ii through the coils 315' and 315 is the phasor sum of the current I 2 through the coil 316 and die current I 3 through die capacitor C, l e Because die current through the capacitor C, I e die current I , leads the current I 2 dirough die coil 316, which is basically an inductive member, it makes the current Ii also leads the current 1 2 That is to say, since the same current Ii passes through the coils 315' and 315, die magnetic dnving forces by these two coils are always in phase with each odier but leading die dnving force produced by die coil 316 by a phase difference decided by die value of die capacitor C In operation, as the shuttle 350 is approaching an axial end position under the joint dnving forces by the diree coils, the two end coils 315' and 315 reverse their current direction before the middle coil 316, tiierefore producing an effective suspension effect which would enhance the effects by the suspension spnng arrangement Because tins effect only happens when the shuttle is close to its end positions, it will not damage die system efficiency, instead it improves the overall efficiency by making the shuttle movement better suspended By selecting a suitable value for the capacitor C, the system can be easily fine-turned to suit a particular application The circuit also includes a protection thermistor R,ι to prevent current surge at start-up and an overheatmg protection circuit including a resistor R, a thermistor R^ and a relay switch S 2 The operation of the protection circuit is conventional so no further descπption is needed General Structure of the Fourth Embodiment Now the fourth embodiment of this invention is descnbed witii reference to a compressor 500 shown in Figs 11 to 15 Many aspects of the compressor 500 and its working pnnciples are similar to tiiat of the earlier embodiments New features include electromagnet pole pieces with flux switching arrangement and pole face extension patterns, an electnc circuit arrangement for generating phase differences in the dnving coils and a revised suspension arrangement The new features are descnbed below in details In Fig 11, the compressor 500 includes a stator 510, a shuttle 550, a pair of end assemblies 530 and 530' and a central guide 520 which secures the whole unit together In operation, process gas would enter chambers I and I' through the stator, then forced by die shuttle into lntercoohng chambers II and II' inside die end assemblies 530 and 530' and tiien enter chambers EQ and ID' to be further compressed and finally forced out through outlet valves in valve blocks 540 and 540' In Fig 12, die central guide 520 and die shuttle 550 have been removed to show die details of die stator 510 and die two end assemblies 530 and 530' The stator 510 has a housing 51 1 of magnetic matenal serving as part of the stator magnetic circuit At each end of the housing 511 is fitted an end pole piece 512 or 512' Three winding coils 515a, 515b and 515c are coaxially arranged inside tlie housing 511 and separated from one another by two annular pole pieces 513 and 513' which have annular pole face with toothed pole face extension pattern 516 and 516' The toothed pattern ensures tiiat the magnetic linkage between tlie shuttle and the stator is improved, especially when die current reverses its direction, by extending die stator's pole face in axial direction, while at the same time avoids excessive flux leakage over die gap by keeping a necessary gap length g between the tootii tips as shown by the arrow sign in Fig 12 The pole pieces also have flux switch arrangement formed by magnets 514 and 514', tiieir working pnnciples are to be further descnbed wrth reference to Figs 14 A to 14E A non-magnetic cylinder 517 is fitted inside the tiiree coils and clamped between the two end pole pieces 512 and 512', defining a cyhndncal inner space for the shuttle 550 Gas inlet holes 524 and 524' are formed on die cylinder 517 in a similar way as in the previous embodiment The assembly 530 has a non-magnetic casing 531 with external fins 532 of thermally conductive matenal, such as aluminium The casing 531 has a flange 533 which matches corresponding flange of die stator housing 511 to ensure precise alignment between them Inside die casing 531 is a second stage cylinder 534 with one end sitting against the end pole piece 512 and die otiier end against the valve block 540 Surrounding die cylinder 534, there is a magnet spnng formed by a winding coil 535 and a pole piece 518 Between die magnet spnng and die casing 531, tiiere is an lntercoohng chamber II with relevant inlet and outlet valve arrangements In Fig 13, die shuttle 550 has a middle pole nng 551 and two middle magnets 552 and 552' fitted on a central tubular member 555 made of non-magnetic matenal To each end of the tubular member 555 is fitted an intermediate pole piece 553 or 553', which holds an end magnets 554 or 554' and an end pole piece 556 or 556' The magnet 554 or 554' and its end pole piece 556 or 556' are fitted on a beanng member 557 or 557' made of plastic or composite beanng matenal which has an annular end part forming a piston face 558 or 558' In operation, the piston face 558 or 558' also provides thermal insulation to prevent the magnets becoming overheated Again, all tiiese magnets are magnetised in axial direction, so each of them fonns an axially exposed magnetic gap along its lengtii between the corresponding pole pieces That is to say, the shuttle 550 has four magnetic gaps to interact with the three gaps formed in die stator As to be further descnbed below, at any particular moment of operation, there would always be three magnetic gaps on the shuttle interacting with the stator while the other one interacts with a magnetic spnng The shuttle 550 is supported by an internal suspension mechanism formed by a central shaft 520 and a pair of mechanical spπngs 525 and 525' The central shaft 520 has a thicker middle portion 522 witii a middle flange 523 supporting tlie spπngs At each end of die middle portion 522 is a thin shaft portion 521 or 521 ' extending through the beanng member 557 or 557' As shown in Fig 11, the other end of die tiun shaft portion 521 or 521 ' extends through the valve block 540 or 540' and tlie whole unit is precisely aligned and secured by bolts The shaft 520 is hollow so that a coolant can be circulated tiirough to keep the whole unit, especially tlie shuttle 550, cooled dunng operation Figs 14A to 14E show the working pnnciples of die flux switching mechanism used in die fourth embodiment In Fig 14 A, when the magnet 514 is fitted into an annular recess formed in the pole piece 513, the flux generated by the magnet 514 fonns a closed circuit through tlie narrow parts 513a and 513b to bnng the flux in these parts close to flux saturation Fig 14B shows a similar flux distnbution generated by a winding coil 514a Since tiiese two alternatives work in similar ways, only tlie one using permanent magnet 514 is to be descnbed below Fig 14C shows the flux distnbution when a shuttle is fitted inside a stator with no current in any of the three coils The flux generated by die switching magnets 514 and 514' and tiiat by the middle magnets 552 and 552' interact with each other to form two closed magnetic circuits, which produce strong registration forces to lock the shuttle to its neutral position where tlie magnetic resistance in each circuit would be die minimum When the stator is energised, as shown in Fig 14D, die flux generated by die magnets 514 and 552 would be linked with tiiat of the coil 515a, so are the magnets 514' and 552' with the coil 515b, producing a combined dnving force towards d e πght-hand side, as shown by die large arrow sign to bottom of the drawing It should be noted here that most of the flux through each of the pole pieces 513 or 513' is switched to the left-hand side half of die extended pole face patterns, leaving no significant flux at the other side When the current reverses direction, as shown in Fig 14E. the flux would be switched by die switching magnets 514 and 514' to the other side of die pole pieces 513 and 513', dnving die shuttle towards die opposite direction By switching the flux from one half of the pole piece to the otiier half in response to the change of the current direction, the magnetic linkage between tlie stator and the shuttle is significantly improved, which allows the shuttle a relatively long stroke under high energy efficiency Fig 15 shows a control circuit for the fourth embodiment In tins circuit, each magnetic spnng coil 535 or 535' is connected to a capacitor in senes, then the two of them is connected with the coil 515a or 515c in parallel, which in turn is connected to the coil 515b in senes Again, the current I] through the coil 515b is the phasor sum of the current I 2 through die coil 515a and die current h through the coil 535, or the phasor sum of the current I' 2 through the coil 515c and die current 1 through the coil 535', l e In tins way, the five coils are divided into three groups having different phase differences, with the coils 535 and 535' leading die coil 515b winch in turn leads die coils 515a and 515c In operation, as the shuttle 550 approaches an end position, the magnetic spnng coil 535 or 535' would have already reversed its current direction to produce a repelling force, which is helped by the coil 515b in die middle to force the shuttle to move backwards Again the system can be fine-turned by selecting suitable value for the magnetic spnng coils 535 and 535' and their associated capacitors General Structure of the Fifth Embodiment Now the fifth embodiment of tins invention is descnbed with reference to a compressor 600 shown in Figs 16A to 20B Many aspects of the compressor 600 and its working pnnciples are similar to tiiat of die earlier embodiments New features include a more compact shuttle assembly design witii a central guide extending tiirough its whole length for precise alignment of its parts, a suspended stator design to ensure the machine's vibration-free operation which also has a cylinder extending tiirough its whole lengtii for its precise alignment, a novel gas flow passage and check valves fitted inside die shuttle's central guide The new features are descnbed below in details In Figs 16A and 16B, the compressor 600 includes a housing 610 formed by a tubular member 611 and two end assemblies 620 and 620', a stator 630 suspended by a pair of disk spnngs 640 and 640' and a shuttle assembly 650 fitted inside die stator with its two ends extending into each of die end assemblies 620 and 620' In Fig 17, the stator and die shuttle assembly have been removed to show the details of die housing 610 The middle section of the housing is formed by the tubular member 611 and the two ends are the end assemblies 620 and 620' secured to the middle section by fastening means 619 The tubular member 611 has outer fins 612 to improve its mechanical strength and heat dissipation The whole member is made of magnetic matenal so that it also serves as part of the stator's magnetic circuit Throughholes 613 and 613' form gas inlet into die housing At each end of the member 611 is a flange 614 or 614' for precise alignment and fastening with the end assemblies 620 and 620' The two end assemblies 620 and 620' are identical so only die assembly 620 is descnbed here The assembly 620 has a non-magnetic and tiiermally conductive body formed by e g aluminium casting The casting has a cyhndncal portion 621 with external fins 622 for heat dissipation and a flange portion 623 with an extended lip 624 for engaging the corresponding flange of die tubular member 611 An elastomer member 625 is fitted inside die lip 624 and covenng die inner surface of the flange portion 623 so that when the machine is assembled a pair of disk spπngs 640 and 640' (not shown in Fig 17) are clamped between the elastomeπc member 625 and an elastomer bushing 615 to ensure a gas-tight fit The elastomer member has a surface which is shaped to match die end portion of the stator so as to provide impact protection to the disk spnng and stator and also to provide tiiermal and noise insulation, as to be descnbed later Inside die cyhndncal portion 621 there is a cylinder liner 626 which, together with a valve block 670, defines a compression chamber Fig 18 shows the structure of the stator 630 and its suspension spπngs 640 and 640' The stator has a non-magnetic cylinder 631 extending tiirough its whole length, defining a cyhndncal inner space for accommodating die middle portion of the shuttle assembly 650 The cylinder 631 can be made of a self-lubncating matenal, preferably a composite matenal with metal or glass fibre re- enforcement for its excellent mechanical strength and good tiiermal conductivity Gas inlet channels and holes 634 and 634' are formed through the pole pieces and die cylinder 631 in a similar way as in die earlier embodiments Surrounding die cylinder 631 are fitted four winding coils 635a, 635b, 635c and 635d, separated from one another by three intermediate pole pieces 633a, 633b and 633c and held together by two end pole pieces 633 and 633' The intermediate pole pieces 633a, 633b and 633c have flux switching magnets as in the previous embodiment Each end pole piece is fitted with a magnetic spnng 636 or 636' which is secured to one end of die cylinder 631 and also provide attachment to the suspension spnng 640 or 604' Inside each magnetic spnng 636 or 636' is fitted a slide beanng/seal member 638 or 638' for beanng the shuttle shaft The disk spπngs 640 and 640' are formed by a lamination of thin metal sheet(s) and non-metal elastomer sheet(s), such as rubber or plastics, so the spπngs also serve as diaphragms dividing die space between die housing 610 and die stator 630 into separated gas-tight chambers, as to be descnbed later The spnngs' stiffness is selected to make the stator's nature frequency close to the frequency of tlie electnc power input In Fig 19, the shuttle assembly 650 has a non-magnetic central guide member in the form of a thin-walled tube 656 which carnes all the other parts and keeps diem precisely aligned The tube 656 can be made of e g stainless steel or titanium The shuttle's middle portion is formed by a senes of magnets and pole pieces including a middle nng magnet 651, two middle pole pieces 652 and 652', two end nng magnets 653 and 653' and two end pole pieces 654 and 654', which carry elastomer bushing 655 and 655' for impact protection The middle portion has a cyhndncal outer surface covered by a self-lubπcating film to form a clearance seal with die cylinder 631 in Fig 18 Inside die tube 656, tiiere are a number of rod magnets 651a, 653a and 653a' and pole pieces 652a, 652a'. 654a and 654a', which fill the space inside die tube and form a very compact design Also fitted inside die tube 656 are two reed valve 660 and 660' which have inlet holes 657 and 657' and outlet holes 658 and 658' for one-way gas flow Each end of die tube 656 is fitted with a piston head 665 or 665', via a universal joint formed by a ball-shaped member 666 or 666' and a joint seat member 664 or 664' The use of the universal joint allows a "loose fit" between the shuttle shaft and die piston head to ensure that in operation the piston head 665 or 665' would not subject to sideways forces so the wear of its sealing surface is minimised Tlie piston head 665 or 665' can be made of self-lubπcating plastics for lubπcant-free operation Using plastic piston also has the advantage that the compression heat is insulated and cannot affect the shuttle's magnets The joint seat member 664 or 664' is an extension of tlie valve 660 or 660', which can be made of a light weight and high strength matenal, such as engineenng plastics or carbon fibre matenal By inserting such a member into the thin-walled tube 656, it significantly improves the shaft's mechanical strength When assembled, the joint seat member also holds a suspension spnng, as in die earlier embodiment The piston head also carnes a one-way valve 667 or 667' allowing gas flow into the compression chamber Figs 20A and 20B show die structure of the reed valve 660 or 660' In Fig 20 A, die valve 660 is foniied by a valve seat 661, a valve reed 662 and outlet member 663 to which the valve reed is attached The valve seat 661 and the outlet member 663 have corresponding angled faces with a small gap formed between them, in which locates tlie valve reed The valve reed is made of dun elastic sheet such as stainless steel or beryllium copper sheet The valve reed is bent along die valve seat's angled face so it is biased by its own elastic force to close the inlet port In operation, the angled face on the outlet member 663 serves as a stopper to prevent the reed to bend too much Fig 20B shows tiiat die valve reed 662 has a spnng stπp 662a and an attachment stnp 662b which would form a circle around die member 663 for a reliable attachment This design ensures that a reliable reed valve can be fitted into die limited space inside a shuttle shaft Now the operation of the compressor 600 is descnbed witii reference to Figs 16A and 16B When die compressor is assembled, the stator 630 is fully suspended by the two disk spπngs 640 and 640' and its outer cyhndncal surface forms a gap with die inner surface of die tubular member 611 which also serves as a part of the stator's magnetic circuit (in Figs 16A and 16B, tins gap is exaggerated to make it easy to see) That is to say, the stator itself does not have physical contact with the housing 610 and is free to vibrate In operation, because both the stator and die shuttle assembly are fully suspended and free to reciprocate, and also because die active and reactive forces between them are always the same in magnitude and opposite in direction, they will cause each other to move in opposite directions to cancel each other's vibrating effects In tins way, the machine as a whole would have virtually no vibration The suspended stator also prevents noise from escaping out of the compressor The result is quiet and vibrati on-free operation The compressor 600 has a double acting design with an internal multistage compression arrangement To each side of die compressor there are four chambers formed between the housing 610, die stator 630 and die shuttle assembly 650, including a muffler chamber I or I' m the housing between die stator and die disk spnng, a first stage compression chamber II or II' inside die stator, an lntentiediate chamber HI or HT between the disk spnng 640 or 640' and die end assembly 620 or 620' and a final stage compression chamber IV or IV' inside each end assembly As shown in Fig 16B, die shuttle assembly 650 is dnven to die left-hand side wlnle the stator 630 is dnven by a reactive force to the nght-hand side At tins position, the chambers II and IV to the πght-hand side suck gas in from the chamber 1 or HI respectively, while to tlie left-hand side die gas in die chamber II' is forced into the chamber HI' via the reed valve 660' and die gas in die chamber IV' is forced out tiirough the valve block 670' That is to say, in addition to vibration-free operation, die stator's movement, though very small, has positive contπbution to the gas compression process Finally, it is worth mentioning that because the inlet gas in the muffler chambers I and Y helps to keep die winding coils and die shuttle magnets cooled, and also because die final stage compression chambers IV and IV' are located away and thermally insulated from the stator, the compression heat generated there would not affect die pennanent magnets on die shuttle, so die motor effi ciency I s high Industrial Applicability It is not difficult to understand from the above descnption tiiat the linear motor and/or compressor according to the present invention has at least tlie following advantages a) High energy efficiency, compact structure and low manufactuπng costs b) High pressure and flow rate output c) Lubπ cant-free, leak-free and maintenance-free operation d) Low noise and vibration-free operation e) Good heat dissipation f) Reliable suspension for long and trouble-free service life Finally, there is no need to mention that the embodiments in tins application are only exemplary, which can be easily adjusted or altered by tiiose skilled in the art once the basic concepts of the invention are understood For example, by combining the first two embodiments, it is easy to achieve tiiree-stage compression within one unit, while in the third and fourth embodiment, it is possible to incorporate more coils in the stator and more magnets in the shuttle to make the motor more powerful and to have a relatively long thin shape for better heat dissipation Furthermore, other impedance elements, such as inductive or resistive types, can be used to produce the phase difference between the winding coils

Claims: Claims 1 A linear motor compπsing a stator having magnetic arrangement forming a plurality of axially exposed magnetic gaps, a reciprocating member, and means for energising said stator and/or reciprocating member, wherein said reciprocating member has magnetic arrangement forming a plurality of axially exposed magnetic gaps for interacting with the magnetic gaps of said stator 2 A linear motor compressor compnsing a housing enclosing an inner space, a stator having magnetic arrangement forming a plurality of axially exposed magnetic gaps, a reciprocating member disposed in said inner space, valve means for forming at least one fluid passage into and out of said inner space, and means for energising said stator and/or reciprocating member, wherein said reciprocating member has magnetic arrangement forming a plurality of axially exposed magnetic gaps for interacting with tlie magnetic gaps of said stator 3 An apparatus of claim 1 or claim 2, wherein said stator and reciprocating member's magnetic gaps are arranged in an interposed relationship 4 An apparatus of any of the preceding claims, wherein tlie magnetic arrangement of said reciprocating member is formed by permanent magnets and/or electromagnets 5 An apparatus of any of the preceding claims, further compnsing central guide means keeping said reciprocating member coaxial with said stator 6 An apparatus of claim 5, wherein said central guide means is hollow to form a passage for circulating a cooling fluid 7 An apparatus of any of the preceding claims, further compnsing a suspension mechanism for said reciprocating member which includes magnetic spnng arrangement 8 An apparatus of claim 7, wherein said magnetic spnng arrangement has a nested permanent magnet and/or electromagnet structure forming flux concentration therein 9 An apparatus of any of the preceding claims, further compnsing elastomenc members for cushioning said reciprocating member 10 An apparatus of any of the preceding claims, further compnsing means for generating phase difference in the flux of said plurality of axially exposed magnetic gaps of said stator and/or reciprocating member 11 An apparatus of claim 10, wherein said phase difference generating means is an impedance element of capacitive, inductive and/or resistive type 12 An apparatus of claim 2 or any of claims 3 to 11 in combination with claim 2, wherein said stator and reciprocating member are arranged to form at least one pre-compressing space and one further compressing space, and a one-way fluid passage is formed therebetween so that a process fluid can be compressed progressively therein 13 An apparatus of claim 12, wherein said further compressing space is formed outside said stator 14 An apparatus of claim 12 or claim 13, further compnsing an lntercoohng space arranged between said pre-compressing space and said further-compressing space 15 A suspension mechanism for a reciprocating member in a linear motor having a stator with pole means for interacting with pole means formed on said reciprocating member to cause the latter to reciprocate between two end positions, wherein said suspension mechanism has magnetic spnng means arranged to interact with the pole means of said reciprocating member to produce a return force in response to its movement towards each said end position 16 An apparatus of claim 15, wherein said magnetic spnng means has a nested permanent magnet and/or electromagnet structure forming flux concentration therein 17 A flux switching mechanism for a linear motor having a stator and/or a reciprocating member with pole means between two adjacent magnetic gaps, wherein said pole means is divide into two axial portions by magnetic means for switching flux from one portion to another in response to the change of die direction of an energising current supplied to said stator and/or reciprocating member 18 A mechanism of claim 17, wherein said flux switching means include permanent magnet means magnetised in axial direction and/or electromagnet means 19 A lmear motor of claιml7 or claim 18, wherein said pole means further compπses means for extending pole face in axial direction 20 A linear motor and/or compressor having a housing accommodating a stator and a reciprocating (shuttle) member, wherein both said stator and reciprocating member are suspended to make them movable relative to said housing so tiiat when in operation the interaction between said stator and reciprocating member would cause diem to reciprocate in opposite direction 21 A linear motor and/or compressor of claim 20, wherein said stator is suspended by disk spnng means to ensure its precise alignment with said housing 22 A linear motor and/or compressor of claim 21, wherein said disk spnng means also act as diaphragm means dividing die space between die stator and die housing into chambers so that the stator's movement would also produce compression effects

Inventors: ZHANG WEI-MIN, ZHANG, WEI-MIN
Applicants: Z & D LIMITED, ZHANG WEI MIN, ZHANG, WEI-MIN
Application year: 1998
Main classification: H02K33
IPC codes: F04B35, H02K7, H02K16, H02K33, H02P25