A machine system of positive displacement, centric reciprocating type

Abstract

A machine system of positive displacement, centric reciprocating machine type, comprising at least two cooperating machines (101; 101'; 101''; 101''') of said machine type, a single rotary main drive shaft (117; 126) providing joint operation of a pair of drive shafts (115; 116) of each machine, said operation being provided by attaching a single non-circular gear (118; 119) to each of the two drive shafts (115; 116) of each machine, and letting the non-circular gears (118; 119) of the machine drive shafts (115; 116) engage with the single and rotary main drive shaft (117; 126) located parallel to the drive shafts (115; 116) of the rotary parts (105; 107; 109; 111; 113 and 106; 108; 110; 112; 114) of the machines either a) via a respective one of first and second non-circular gears (127; 128) on the rotary main drive shaft (126), or b) via a non-circular rotary gear (120) rigidly attached to a circular gear (123) rotatably engageable with a respective one of the first and second circular main gears (124; 125) on the rotary main drive shaft (117).

Description

[0001] A machine system of positive displacement, centric reciprocating type

[0002] Background of the invention

[0003] The present invention relates to a machine system of positive displacement, centric reciprocating machine type, as defined in the preamble of claim 1. Such a machine type comprises:

[0004] - a non-rotatable housing which surrounds a pair of first and second mutually movable rotary parts having co-axial rotary axes of rotation, the housing exhibiting an inner, circular curved surface and two planar, parallel inner end wall surfaces,

[0005] - a pair of drive shafts for the rotary parts extending in mutually opposite directions, and

[0006] - fluid inlets and outlets selectively communicating with adjustable angular spaces created by mutual rotary movement of the first and second rotary parts within the housing.

[0007] Prior art

[0008] Partially related prior art is found e.g. in US 4.901,694, US 903,470, WO 2014 / 112,885 (belonging to the applicant) and NO-application 20231344 (belonging to the applicant). Other, but far less related prior art is found in US 3,112,062; US 1,568,053; US 2,628,014; US 836,430; US 2007 / 062,482; US 3,193,191; WO 2013 / 071,845; WO 0,134,944; US 3,396,632; EP 0,034,085; US 2,155,249; ES 2,756,876; US 2007 / 245,727; US 7,283,373; and US 2018 / 313,261.

[0009] Objects of the invention

[0010] Although in the prior art related to compressors it is common practise to make use of a gradual stepping-up of the pressure until final output, it is a recurring issue having to provide the compressor with a simple structure and which requires little or no lubrication in conjunction with pressure-sealing. Most of all as regards compression machines, it is important that the gas to be compressed is not contaminated by any sealing liquid, such as e.g. oil. Furthermore, it is for some applications desirable to reduce pressure fluctuations at the compressor output. One object of the invention is to make use of at least two machines of said type in order to provide for a stepwise increase or decrease in pressure output from each machine stage in the system of interconnected and cooperating machines and with the advantageous use of just one drive shaft to operate the machines of the system.

[0011] Another object of the invention is to make use of at least two machines of said type in order to provide for a smoothened or fluctuation-less common compression pressure output from the system of interconnected and cooperating machines and with the advantageous use of just one drive shaft to operate the machines of the system.

[0012] Summary of the invention

[0013] According to the invention, the system as defined in the “Background of the invention” section and in the preamble of claim 1 has its distinctive features, wherein the system comprises at least two cooperating machines of said machine type, wherein a single rotary main drive shaft, located parallel to the drive shafts of the rotary parts, provides coordinated joint operation of the at least two machines and a coordinated joint operation of the pair of drive shafts of each machine of the at least two machines, wherein the coordinated joint operation of the pair of drive shafts of the at least two machines is provided by attaching a single non-circular gear to each of the two drive shafts of each machine, and wherein the non-circular gears of the drive shafts of each of the at least two machines engage with the single and rotary main drive shaft located parallel to the drive shafts of the rotary parts either a) via a respective one of single first and second non-circular gears on the rotary main drive shaft, or b) via a non-circular rotary gear rigidly attached to a circular gear rotatably engageable with a respective one of single first and second circular main gears on the rotary main drive shaft.

[0014] It will be appreciated that the main drive shaft can be powered from or delivering power to a power device, e,g. a motor or generator.

[0015] Suitably, the non-circular gears are oval or elliptical. These and further features of the invention will appear from the subsequent detailed description with reference to the attached drawings, as well as highlighted features in the claims.

[0016] Brief description of the drawings

[0017] Fig.l shows a perspective view the system having two machines with a single common drive shaft, however with fluid interconnections between the machines not shown for sake of clarity.

[0018] Fig.2 shows another perspective view the system as shown in Fig.l.

[0019] Fig. 3 shows in another perspective view the system of Fig. 1, shown from an opposite end of the drive shaft and from a different angle.

[0020] Fig. 4 shows in another perspective view the system as depicted on Figs. 1 and 2, and from the opposite end compared to Fig. 3.

[0021] Fig. 5 is an end view of the system as seen from the right-hand end of Figs. 1, 2 and 4.

[0022] Fig. 6 is an end view of the system as seen from the right-hand end of Fig. 3.

[0023] Fig. 7 shows in a perspective view a modification of the embodiment shown on Figs.l - 4 with three machines in interaction.

[0024] Fig. 8 shows in a perspective view a further modification of Figs. 1 - 4 and 7 with four machines in interaction.

[0025] Fig. 9 shows an end view of the system as seen from the right hand end of Fig. 7.

[0026] Fig.10 is an end view of the system of Fig.7 as seen from the left hand end of Fig.7.

[0027] Fig. 11 shows an end view of the system as seen from the right hand end of Fig.8. Fig, 12 is an end view of the system of Fig. 8 as seen from the left hand end of Fig. 8

[0028] Fig. 13 shows in a perspective view a modification of the embodiment shown on Figs. 1 - 6, but with different arrangement of drive gears.

[0029] Fig. 14 is a perspective view of a modifications of the system of Fig. 13 and showing joint operation of three machines in the system like in Fig.7, but with different arrangement of drive gears.

[0030] Fig. 15 is an end view of the system of Fig. 13, as viewed from the right-hand end thereof.

[0031] Fig. 16 is an end view of the system of Fig. 13, as viewed from the left-hand end thereof.

[0032] Fig. 17 is another perspective view of the embodiment of Fig. 13, shown in a slightly different operational position of the common drive shaft.

[0033] Fig. 18 is a perspective view of the embodiment of Fig. 17 shown from the other end of the common drive shaft.

[0034] Fig. 19 shows in a perspective view how the system may be expanded to comprise four cooperating machines having a common a drive shaft.

[0035] Fig. 20 shows in a different perspective view the embodiment of Fig. 19.

[0036] Fig. 21 shows in a perspective view how the system may be expanded to comprise six cooperating machines having a common a drive shaft.

[0037] Fig. 22 is a variant of the embodiment of Fig. 21.

[0038] Fig. 23 shows in a perspective view how the system may be expanded to comprise nine cooperating machines having a common a drive shaft.

[0039] Fig. 24 shows in a perspective view a machine of the system with drive shafts related to the rotary parts of the machine and non-circular gears at the ends the drive shafts. Fig. 25 shows in a perspective, partially sectioned view an internal structure of the machine of Fig. 24 showing its two internally located rotary parts, and with a first type of pressure sealing.

[0040] Fig. 26 shows in a perspective, partially sectioned view an internal structure of the machine of Fig. 24 showing its two internally located rotary parts, and with a second type of pressure sealing.

[0041] Fig. 27 shows in a perspective, partially sectioned view an internal structure of the machine of Fig. 24 showing its two internally located rotary parts, and with a third type of pressure sealing.

[0042] Fig. 28 shows in a perspective, partially sectioned view an internal structure of the machine of Fig. 24 showing its two internally located rotary parts, and with a fourth type of pressure sealing.

[0043] Fig. 29 shows in a perspective, partially sectioned view an internal structure of the machine of Fig. 24 showing its two internally located rotary parts, and with a fifth type of pressure sealing.

[0044] Fig. 30 shows in a perspective view one of the two identically structured, co-operating rotary parts inside the machine, and being related to the embodiment as shown on Fig. 25.

[0045] Fig. 31 shows in a perspective view one of the two identically structured, co-operating rotary parts inside the machine, and being related to the embodiment as shown on Fig. 26.

[0046] Fig. 32 shows in a perspective view one of the two identically structured, co-operating rotary parts inside the machine, and being related to the embodiment as shown on Fig. 27.

[0047] Fig. 33 shows in a perspective view one of the two identically structured, co-operating rotary parts inside the machine, and being related to the embodiment as shown on Fig. 28.

[0048] Fig. 34 shows in a perspective view one of the two identically structured, co-operating rotary parts inside the machine, and being related to the embodiment as shown on Fig. 29. Fig. 35 is a schematic diagram showing as a non-limiting example a layout of three interconnected and co-operating machines in a compressor pressure stepping-up configuration, and with accessories to be in particular useful with the embodiments on Figs. 27, 28, 32 and 33.

[0049] Fig. 36 is a schematic diagram showing as a non-limiting example a layout of four interconnected and co-operating machines in a pump pressure smoothing output configuration.

[0050] Detailed description

[0051] The embodiment on Figs. 1 - 12 is shown, as a non-limiting example with alternatives of two, three and four machines in the system. However, it will be appreciated that the embodiment may be modified to include more machines using both non-circular and circular gears to yield e.g. six, eight, nine or more machines having a common drive shaft. The embodiments on Figs. 13 - 23 propose the system, which in this case has only non-circular gears, to have -as a non-limiting example - two, three, four, six or nine machines.

[0052] The configuration of the machines, location of inlets and outlets thereon, and proportional size of the circular gears and the circular gears may be varied dependent on the external size and configuration of the machines used in the system. Further, the physical dimension of the machines in a system may mutually vary, dependent on pressure and pressurized volume considerations.

[0053] Further, the examples of pressure sealing as shown on Fig. 25 - 29 and the details of the rotary parts as shown on Fig. 30 - 34 should not be construed as to limiting the scope of the invention.

[0054] As shown in a first non-limiting example of the invention, as shown on Figs 1 - 6, the system comprises at least two machines 101 of positive displacement, centric reciprocating type.

[0055] Each machine comprises, as known in the prior art a non-rotatable housing 102 which has fluid inlets 103 and outlets 104 (only one of each shown on the drawings). The housing 102 surrounds a pair of first and second mutually movable rotary parts 105, 106; 107, 108; 109; 110; 111; 112; 113; 114 (see Figs. 20 - 24, and Figs. 25 -29 ) having co-axial rotary axes, the housing exhibiting an inner, circular curved surface and two planar, parallel inner end wall surfaces.

[0056] Further, each machine has a pair of drive shafts 115; 116 for the rotary parts 105, 106; 107, 108; 109; 110; 111; 112; 113; 114 extending in mutually opposite directions. The fluid inlets 103 and outlets 104 selectively communicate with adjustable angular spaces (not shown) created by mutual rotary movement within the housing of the first and second rotary parts 105, 106; 107, 108; 109; 110; 111; 112; 113; 114.

[0057] An important aspect of the invention is that the system comprises at least two co-operating machines 101 of said machine type.

[0058] In the embodiment as illustrated on Figs. 7, 9 and 10, the system exhibits three co-operating machines 101 of said machine type.

[0059] In the embodiment as illustrated on Figs. 8, 11 and 12, the system exhibits four co-operating machines 101 of said machine type.

[0060] Further, according to the invention and irrespective of the number of machines being two or more, the system makes use of a single rotary main drive shaft 117 , located parallel to the drive shafts 115; 116 of the rotary parts 105, 106; 107, 108; 109; 110; 111; 112; 113; 114, and the main drive shaft 117 provides coordinated joint operation of the at least two machines 101 and a coordinated joint operation of the pair of drive shafts 115; 116 of each machine 101 of the at least two machines. The coordinated joint operation of the pair of drive shafts 115; 116 of the at least two machines 101 is provided by attaching a single non-circular gear 118; 119 to each of the two drive shafts 115; 116 of each machine 101.

[0061] In the embodiment as shown on Figs. 1 - 12 the non-circular gears 118; 119 of the drive shafts 115; 116 of each of the at least two machines 101 communicate with the single and rotary main drive shaft 117 located parallel to the drive shafts 115; 116 of the rotary parts 105, 106; 107, 108; 109; 110; 111; 112; 113; 114 via a non-circular rotary gear 120; 121 rigidly attached to a circular gear 122; 123 rotatably engageable with a respective one of single first 124 and second 125 circular main gears on the rotary main drive shaft 117. The use of circular gears enables to have different rpm’s (revolutions per minute) and momentum on the rotary parts 105, 106; 107, 108; 109; 110; 111; 112; 113; 114 relative to the rpm of the main drive shaft. A further advantage is the possibility of optimizing the dimensions or “diameter” of the non-circular gears which are used for an optimized overall performance of the system.

[0062] The embodiments of Figs. 13 - 24 are now to be further described.

[0063] The embodiment of Figs. 13 and 15 - 18 exhibit two machines 101, each with inlets and outlets 103; 104, separate drive shafts 115; 116 for the rotary parts (not shown on on the figures) and a common rotary main drive shaft 126. The main drive shaft 126 has a pair of non-circular gears 127; 128 to engage non-circular gears 118; 119 on the drive shafts 115; 116 of the rotary parts of the machines 101 in order to obtain coordinated operation of the rotary parts of each machine and also the mutual operation of the two machines.

[0064] The novel approach of Figs. 13 - 23 is thus to enable the single rotary main shaft 126 to be able to operate at least two machines through use of its non-circular gears 127; 128 engaging the non-circular gears 118; 119 on the drive shafts 115; 116 of the machine. For most intents and purposes when arranging machines in a radial type of layout, two, three or four machines would be a first choice. Choosing a layout of three or four radially disposed machines would likely require an increased interspace of the machines and increased size of the non-circular gears, in order for the non-circular gears 127; 128 to be able to engage all of the non-circular gears 118;119 of the four machines 101, respectively.

[0065] As non-circular gears are expensive and require accurate dimensional construction, it would be of advantage to standardize their size. In the context of the present invention, the non- circular gears are oval or elliptical.

[0066] It will be appreciated that the main drive shaft 117; 126 can be powered from or delivering power to a power device (not shown), e.g. a motor or generator.

[0067] In the embodiment of Fig. 14 the common main drive shaft 126 is capable of operating or coordinating operation of three machines 101. Figs. 15 and 16 shows end views of the embodiment, involving two machines 101, as shown in Figs. 13, 17 and 18.

[0068] The embodiment in Figs. 19 and 20, as well as Figs. 21 - 23 illustrate another aspect of the invention, wherein there are m machines present in the system, wherein there are n groups of machines in longitudinal direction of the main drive shaft, each group thereby exhibiting m / n radially aligned machines, and wherein each group of machines communicate with an assigned set of single first and second main gears on the main drive shaft. This approach will be valid irrespective of whether there is used a combination of inter-engagement of noncircular and circular gears, as explained in connection with Figs. 1 - 12, or the sole interengagement of just non-circular gears.

[0069] In the non-limiting examples of Figs. 19 - 23, in Figs. 19 and 20 m = 4 and n = 2; in Figs. 21 and 22 m = 6 and n = 2; and in Fig. 23 m = 9 and n = 3.

[0070] It should be noted on Fig. 22 that at the middle region of the system the non-circular gear 128 engages the three non-circular gears 119 (only two visible), and the non-circular gear 127 engages the non-circular gears 118. However, in the embodiment of Fig. 21, the adjacent non-circular gears 127, 128 are located to have the same instantaneous orientation, thus yielding that adjacent pairs of non-circular gears 118, 119 will have a common orientation, respectively. Thus, the gears 127, 128 could be joined into a single gear 129, and each of the pair of gears 118, 119 into a respective common gear 130, respectively.

[0071] A similar approach as that on Fig. 21 is observed on Fig. 23.

[0072] Although the structure of a machine of positive displacement, centric reciprocating type is generally well known in the art, for sake of completeness, the structure of the machines 101 will be briefly explained. In each machine 101 a first one 105; 107; 109; 111; 113 of the rotary parts has a hub 131 and at least two wings 132, 133 extending radially therefrom in mutually opposite directions, the radially outermost end of the wings 132, 133 having a curved configuration 134 to be controllably movable along an inner circular curved wall surface 135 of the housing 102, and with two other opposite, parallel wing regions 136 , 137 movable relative to the flat inner end wall surfaces 138, 139 of the housing 102. Similarly, the second one 106; 108; 110; 112; 114 of the rotary parts has a hub 131 and at least two wings 132, 133 extending radially therefrom in mutually opposite directions, the radially outermost end of the wings having a curved configuration 134 to be controllably movable along the inner circular curved wall surface 135 of the housing 102, and with two other opposite, parallel wing regions 136, 137 movable relative to the flat inner end wall surfaces 138, 139 of the housing 102, and each of the inlets 103 and outlets 104 of the machine 101 communicating with successive ones of four adjustable angular spaces 140 between a pair of the wings 132; 133 of the first rotary part 105; 107; 109; 111; 113 and the second rotary part 106; 108; 110; 112; 114. The axial dimension of the hubs 131 of the first and second rotary parts is normally a half of the axially directed thickness of the wings 132, 133 of the first and second rotary parts.

[0073] As noted from Figs. 25 - 29 and in more detail from Figs. 30 - 34, each machine has pressure seal devices configured on the rotary parts 105, 106; 107, 108; 109, 110; 111, 112; 113, 114 to provide a pressure sealing between the rotary parts and adjacent curved 135 and planar 138, 139 faces of the interior of the machine housing 102 by use of one of: a) seal members 141 attached to the rotary parts 105; 106 on the wings 132, 133 to be slideable along the curved 135 and planar 138; 139 inside faces, as shown on Figs. 25 and 30, such seal members being well known in the art, and are suitably made from metal, rubber, plastics or a composite material; b) labyrint seal 142 or so-called pressure drop or trap grooves engraved into to the rotary parts 107; 108 on the wings 132, 133 thereof to be movable in spaced relationship along the curved 135 and planar 138; 139 inside faces of the housing 102, as shown on Figs. 26 and 31, and such a kind of seal being well known from e.g

[0074] WO 2014 / 112,885. Labyrinth sealing implies that there is no mechanical contact between the rotary parts and the inside walls of the housing. As a supplement to or as an alternative to having labyrinth seals on the rotary parts, labyrinth seals of the type shown at 142 could be located on the inside walls of the housing. If both on the rotary parts and on the inside walls, improved pressure sealing may be obtainable, however likely at an increased cost; c) rotor liquid injection seal apertures 143, as shown on Figs, 27 and 32, located at end regions of the walls of the hub 131 and wings 132; 133 of the rotary parts 109; 110 to allow sealing liquid from inside of the rotary parts 109; 110 to exit from said apertures (or small holes), such sealing liquid having to be continuously delivered to the inside of the rotary part. The liquid may also act as a kind of lubrication to avoid metal-against-metal contact between the rotary parts 109; 110 and the inside walls 135; 138; 139 of the housing; d) liquid seal apertures 144 as shown on Figs. 28 and 33, using sealing liquid appearing from interior of the rotary parts, located at end face regions of the hub 131 and wings 132; 133 of the rotary parts 111; 112 to allow sealing liquid from inside of the rotary parts 111; 112 to exit from said apertures, such sealing liquid having to be continuously delivered to the inside of the rotary parts. The liquid may also acts as a kind of lubrication to avoid any metal-against-metal contact between the rotary parts 111; 112 and the inside walls 135; 138; 139 of the housing 102. This kind of sealing approach is simpler and cheaper than the sealing approach described at item c) above, and is described in more detail and with a variant thereof in NO patent application 20231344 , or e) narrow gap seal 145, as indicated on Figs. 29 and 34, provided by making the faces 145 of the hub 131 and wings 132, 133 of the rotary parts 113; 114 smooth, so as to yield a narrow gap between the rotary parts 113; 114 and the hubs thereof, as well as between the exterior faces of the wings and said internal smooth walls 135; 138; 139 of the housing 102.

[0075] As regards the sealing option of c) above, it is conceivable to use the principles of sealing liquid delivery into the rotary parts as described in NO patent application 20231344 and to cause subsequent exit of the sealing liquid through the apertures 143.

[0076] According to the invention, and as will be further explained in connection with Fig. 35, the outlets of one machine in a deployment of at least two machines are linked by pipes or hoses to respective inlets of next machine in an array of the deployment, to yield a series connection of outlets to inlets in the array of machines. Series connection of multiple compressors or machines, are normally termed as “compressor stages”. The same amount of fluid (normally a gas) weight per second passes through all stages. The compressible fluid is however reduced in volume per stage due to increased pressure, yielding that internal volume for each machine is reduced along the chain of machine stages. Thus, the first machine has a low pressure and large volume, and the next stage(s) will have successively increased pressure and lower volume.

[0077] On the drawings, all of the machines have been depicted with the same size. In the context of a multistage compression operation, each successive machine in the array of series interconnected machines will normally exhibit a smaller size than the preceding machine in the array. The advantage of multistage compressor stages is the avoidance of a large volume and a high pressure combination, which will require very thick walls and / or high strength materials. Further, having a very large compression in one machine instead of dividing a large compression range into multiple stages performed by multiple machines doing a stepwise compression will also yield extreme operational temperatures, heavy loads on the compressor machines and associated driving motors and their structural components, in addition to inter alia causing very low volumetric efficiency and very low isentropic efficiency.

[0078] It will thus be appreciated that in one operational mode the system is configured as a compressor, each machine of the system providing a pressure increase. This will be briefly explained with reference to Fig. 35. It will, however, be appreciated that it may also be desirable to arrange pump machines serially, as well as expander machines.

[0079] In another operation mode of the system, the outlets of all machines in the system are interconnected to yield a common outlet exhibiting reduced pulsation of output pressure by the output of the machines of the system being phase shifted. This is shown in Fig. 36. This can normally be put to practise e.g by distributing the machines of the system with a mutual angle or adjusting “alignment” of wings of the rotary and / or by adjustment of their associated non-circular gears.

[0080] In the case of m identical machines arranged in parallel and each machine producing p

[0081] , , . , , , . 360 , pressure pulses per revolution, a phase shift a between each machine of a = degrees could be suitable in many cases to minimise total system pressure pulses as well as minimising the common drive motor torque load variation. E.g. for 4 machines, each machine having 4 pressure pulses per revolution the phase shift angle would be 22.5 degrees according to the formula above.

[0082] In the case of different machines arranged in parallel, e.g. different in terms of pressure pulse amplitude and or frequency and or different motor torque load, an analysis must be carried out to decide the best phase shifts to optimise the total system pressure pulse variation and motor torque variation. Any phase shift and variation of phase shifts between machines is possible. For the sake of simplicity on Figures 1 - 4, 7, 8, 13, 14 and 17 - 23 these figures do not show how the machines 101 of a system can be interconnected. This will now be explained, merely as a non-limiting example, with reference to Figs. 35 and 36.

[0083] On Fig. 35 is seen how e.g. three machines 101, 101’ and 101” can be interconnected in series by use of their inlets 103, 103’, 103” and outlets 104, 104’, 104”. As an outset, this is valid for all variants fluid pressure seals according to items a) through e). However, if the fluid pressure sealing is according to items c) and d) above and related to Figs. 27 and 32, and Figs. 28 and 33, auxiliary equipment may be required, both to provide pressure sealing by liquid sealing and some cooling effects on the rotary parts and the housing 102 of the machines 101 - 101”.

[0084] Gas 146 to be compressed is delivered at inlet 103. Sealing liquid, e.g. water, is delivered from a supply 147 via a pump 148 and via respective solenoid valves 149, 149’, 149” associated with a respective machine 101, 101’, 101” to a respective liquid or water separator 150, 150’, 150” which is configured to separate liquid, e.g. water, from the compressed gas 146, as well as acting as an output pulsation damper. The liquid is sealing liquid of which a fraction has mixed with the compressed gas. The separated liquid is the delivered back to the respective machine 101, 101’ and 101” via a heat exchanger 151, 151’, 151” and a pump 152, 152’, 152”, respectively. The heat exchanger suitably makes use of cooling water 153; 153’; 153” to cool the separated liquid. A respective level transmitter 154; 154’; 154” is associated with a respective one of the separators 150, 150’, 150” and is used to detect level of separated sealing liquid, and if below or above a threshold value, either to open or close an associated one of the solenoid valves 149, 149’, 149”. If any of the solenoid valves 149, 149’, 149” open to supply more or top up sealing liquid, a common solenoid valve 155 for liquid return or drainage is kept closed, but if the liquid level is above or too close to an upper threshold level in any one of the separators 150, 150’, 150”, the associated one of the solenoid valves 149, 149’, 149” will open, as will also the solenoid valve 155 until rated level is reached. Finally, the gas having passed through the three compressor stages as shown will exit at an outlet 156 from the separator 150” if the liquid sealing approach according to item c) or item d) is used.

[0085] If the sealing approach according to items a), b) or e) is used, then the auxiliary equipment 147 through 155 is not used, and the finally compressed gas exits at outlet 104”. However, in this case, auxiliary dampers, such as pulsation dampers, gas cooling (intercooler devices between adjacent machines, and aftercooler after the last machine in the array may be required or recommended.

[0086] The pressure sealing of type a) above may involve lubrication by oil and thus require separation of oil from the gas between each stage in the system and at the exit from the last stage. Thus, in case of sealing options a), b) or e), auxiliary equipment may be provided as indicated, but in a manner different from the detailed layout on Fig. 35.

[0087] As a further comment to the sealing options a) - e): a) implies lubrication by oil or without liquid, and in either case a cooling of the gas will be required after each stage in the system. As indicated above, if oil is used then both oil separation and oil cooling will be required. b) having labyrinth implies contact free movement and liquid free (oil free). However, cooling of the gas after each stage will be normally required. c) and d) are substantially equal as regards separation, cooling etc, i.e. as shown and described with reference to Fig. 35. e) may be liquid free, although will require in such a case gas cooling after each stage, or it may include liquid in the machine (including oil), and if so both liquid separation, liquid cooling and optionally gas cooling may be required

[0088] Finally, on Fig. 36 is shown, as a non-limiting example, how four machines 101, 101’, 101”, 101”’ may be connected in parallel to yield a smoothened pressurized gas or liquid output 157 based on gas or liquid input delivered at 157.

[0089] An effect inherent with the inventive systems is that when multiple machines are phase shifted, a much smoother loading on a motor driving the main drive shaft will be obtainable, or conversely the loading on a generator when it is powered by the system. This will be possible both fior the series arrangement as indicated on Fig.35 and the parallel arrangement as shown on Fig. 36.

[0090] Finally, the inventive concept of the proposed system, has the advantage of providing a simpler solution than offered by prior art solutions. The use of a single main drive shaft implies that the system can be powered by just a single motor instead of powering each machine by a smaller motor, rendering the system less expensive.

[0091] From viewing Fig, 17, it will be appreciated that powering just one machine will require four non-circular gears, whereas e.g. Fig. 23 showing nine machines in interaction exhibits sixteen non-circular gears, yielding just 1.8 non-circular gears per machine, i.e. less than one half of gears required per machine. In the embodiments of Figs. 21 and 22, there are six machines and twelve and sixteen gears respective, yielding 2 and 2.67 gears per machine, respective. In the embodiment of Figs. 19 and 20, there are four machines in interaction and twelve gears are used, yielding 3 non-circular gears per machine. The same applies for the embodiment of Figs. 13 - 18. Thus, there is any case a considerable saving in the cost of expensive non- circular gears, as well as number of drive motors required, or generators required if the system is to power a generator.

[0092] If the system makes use on circular gears in addition to non-circular gears, as shown on Figs. 1 - 12, the number of non-circular gears per machine will be 4 in all embodiments, but the advantage is still a single main drive shaft and the necessity of just one drive motor or one generator (if the system is generating power). Thus, if using circular gears on the main drive shaft 117, the number of radially located machines may even be increased beyond four. If required, the size of the centrally located circular gears on the main drive shaft may be increased relative to radially located circular gears to yield sufficient space for a desired number of radially located machines. As an outset, there is no limit to the number of radially located machines. Further, there is no limit to the groups of machines possible to arrange in axial direction, all groups having a single, common main drive shaft 117. It will be appreciated, with a mere reference to Fig. 23 and it principles, related to gears 130, transferred to the system using circular gears and non-circular gears, that the number of non-circular gears may be reduced to be less than on average 4 per machine, if multiple groups are axially arranged.

[0093] It will be appreciated that the systems made possible by the invention may be applied to use mainly as compressor, vacuum pump or pump, and further also use as expander.

Claims

CLAIMS1. A machine system of positive displacement, centric reciprocating machine type, the machine type comprising:- a non-rotatable machine (101) housing (102) which surrounds a pair of first and second mutually movable rotary parts (105, 106; 107, 108; 109, 110; 111, 112; 113, 114) having coaxial rotary axes of rotation, the housing exhibiting an inner, circular curved surface (135) and two planar, parallel inner end wall surfaces (138; 139),- a pair of drive shafts (115; 116) for the rotary parts (105, 106; 107, 108; 109, 110; 111, 112; 113, 114) extending in mutually opposite directions, and- fluid inlets (103; 103’; 103”) and outlets (104; 104’; 104”) selectively communicating with adjustable angular spaces (140) created by mutual rotary movement of the first and second rotary parts (105, 106; 107, 108; 109, 110; 111, 112; 113, 114) within the housing (102), wherein the system comprises at least two cooperating machines (101; 101’; 101”;101’”) of said machine type, wherein a single rotary main drive shaft (117; 126), being powered or delivering power, is located parallel to the drive shafts (115; 116) of the rotary parts, provides coordinated joint operation of the at least two machines (101; 101’; 101”; 101’”) and a coordinated joint operation of the pair of drive shafts (115; 116) of each machine of the at least two machines (101; 101’; 101”; 101’”), wherein the coordinated joint operation of the pair of drive shafts (115; 116) of the at least two machines (101; 101’; 101”; 101’”) is provided by attaching a single non-circular gear (118; 119) to each of the two drive shafts (115; 116) of each machine, and wherein the non-circular gears (118; 119) of the drive shafts (115; 116) of each of the at least two machines (101; 101’; 101”; 101’”) engage with the single and rotary main drive shaft (117; 126) located parallel to the drive shafts (115; 116) of the rotary parts either a) via a respective one of single first and second non-circular gears (127; 128) on the rotary main drive shaft (126), or b) via a non-circular rotary gear (120; 121) rigidly attached to a circular gear (122; 123) rotatably engageable with a respective one of single first and second circular main gears (124; 125) on the rotary main drive shaft.

2. The system of claim 1, wherein the non-circular gears (118; 119; 120; 121; 127; 128) are oval or elliptical.

3. The system of -claim 1 or 2, wherein in each machine (101) the first one of the rotary parts (105; 107; 109; 111; 113) has a hub (131) and at least two wings (132, 133) extending radially therefrom in mutually opposite directions, the radially outermost end of the wings (132, 133) having a curved configuration (134) to be controllably movable along an inner circular curved wall surface (135) of the housing (102), and with two other opposite, parallel wing regions (136; 137) movable relative to the flat inner end wall surfaces (138; 139) of the housing (102), wherein the second one of the rotary parts (106; 108; 110; 112; 114) has a hub (131) and at least two wings (132; 133) extending radially therefrom in mutually opposite directions, the radially outermost end of the wings (132; 133) having a curved configuration (134) to be controllably movable along the inner circular curved wall surface (135) of the housing (102), and with two other opposite, parallel wing regions (136; 137) movable relative to the flat inner end wall surfaces (138; 139) of the housing (102), wherein each of the inlets (103) and outlets (104) of the machine (101) communicating with successive ones of four adjustable angular spaces (140) between a pair of the wings (132; 133) of the first rotary part (105; 107; 109; 111; 113) and the second rotary part (106; 108; 110; 112; 114), and wherein an axial dimension of the hubs (131) of the first and second rotary parts (105; 107; 109; 111; 113 and 106; 108; 110; 112; 114) being a half of the axially directed thickness of the wings of the first and second rotary parts.

4. The system of any one of claims 1 - 3, wherein the outlets (104; 104’) of one machine in a deployment of at least two machines (101; 101’; 101”) are linked by pipes or hoses to respective inlets (103’; 103”) of next machine in an array of the deployment, to yield a series connection of outlets to inlets in the array of machines.

5. The system of claim 4, wherein a next machine (101’; 101”) in the array is configured to deliver a higher output pressure than a preceding machine (101; 101’) in the array.

6. The system of anyone of claims 1 - 5, wherein the system is configured as a compressor, each machine (101; 101’; 101”) of the system providing a pressure increase.

7. The system of anyone of claims 1 - 3, wherein the outlets of all machines (101; 101’; 101”; 101’”) in the system are interconnected in parallel to yield a common outlet exhibiting reduced pulsation of output pressure.

8. The system of anyone of claims 1 - 7, wherein all of the machines in a group are radially aligned.

9. The system of anyone of claims 1 - 8, wherein there are m machines present in the system, wherein there are n groups of machines in longitudinal direction of the main drive shaft, each group thereby exhibiting m / n radially aligned machines, and wherein each group of machines communicate with an assigned set of single first and second main gears on the main drive shaft.

10. The system of anyone of claim 1 - 9, wherein each machine has pressure seal devices between the rotary parts and adjacent curved and planar faces of the interior of the machine housing by use of one of: a) seal members (141) attached to the rotary parts slidable along the curved and planar faces, b) labyrinth seal (142), such as pressure drop or trap grooves, c) rotor liquid injection seal (143), d) liquid seal (144) using sealing liquid appearing from interior of the rotary parts, or e) narrow gap seal.

11. The system of claim 10, wherein the seal members (141) of item a) are made from metal, rubber, plastics or a composite material.

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