WO2004044423A1 - Compressor head - Google Patents
Compressor head Download PDFInfo
- Publication number
- WO2004044423A1 WO2004044423A1 PCT/GB2003/004699 GB0304699W WO2004044423A1 WO 2004044423 A1 WO2004044423 A1 WO 2004044423A1 GB 0304699 W GB0304699 W GB 0304699W WO 2004044423 A1 WO2004044423 A1 WO 2004044423A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- head
- chamber
- reciprocating
- compressor
- compressor head
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
- F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
- F04B35/045—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric using solenoids
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/125—Cylinder heads
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B43/00—Machines, pumps, or pumping installations having flexible working members
- F04B43/0009—Special features
- F04B43/0054—Special features particularities of the flexible members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B43/00—Machines, pumps, or pumping installations having flexible working members
- F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
- F04B43/04—Pumps having electric drive
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B45/00—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids
- F04B45/04—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having plate-like flexible members, e.g. diaphragms
- F04B45/043—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having plate-like flexible members, e.g. diaphragms two or more plate-like pumping flexible members in parallel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B45/00—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids
- F04B45/04—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having plate-like flexible members, e.g. diaphragms
- F04B45/047—Pumps having electric drive
Definitions
- This invention relates to a compressor/pump head.
- linear compressors and pumps including both diaphragm type and free- piston type, have become more and more popular.
- Reasons for their success include at least low costs, high efficiency, good reliability, good service life and lubricant-free operation. It is known that linear motors in such machines tend to have strokes variable with changes in electric power input or fluid dynamic load. More particularly, when input voltage rises or outlet pressure drops, a linear motor would stroke longer, which may lead to over- stroke and cause damages by direct impact. On the other hand, when outlet pressure rises or input voltage drops, the linear motor would under-stroke, leaving a large dead space inside the working chamber without producing useful output. For these reasons, linear compressors and pumps are considered not suitable to high-pressure applications.
- a first object of this invention is to provide an improved compressor/pump head more suitable to a linear system.
- a compressor head comprising: a reciprocating (piston) member and a chamber-head member defining a working chamber between them; means for connecting the reciprocating member to a reciprocating drive; and valve means for one way fluid flow into and out of the working chamber; wherein the reciprocating and chamber-head members have complementary surfaces and at least one of these two members has a compliant portion for forming a progressive contact when the reciprocating member approaches the chamber head member.
- the compressor head can achieve a high compression ratio by a relatively small stroke. Also, because the final compression is by a small surface area, it can achieve a high output pressure without a proportional increase of load on the drive.
- both the reciprocating and chamber-head members have flexible portions to allow “soft” contact and to ensure good cushioning when the parts make compliance contacts. Such "soft” contact would ensure low working noise, long service life and also minimum dead space in working chamber, which would lead to high efficiency.
- fluid and/or elastomer cushioning arrangements in reciprocating and/or chamber head structures to provide extra impact protection. It is advantageous that the fluid cushioning is formed by a space closed by bellow means.
- a further object of this invention is to provide a compressor head with a build-in mechanism to adjust its working chamber's size by moving the chamber-head's position in response to outlet pressure changes, so as to compensate the changes in a linear drive's stroke.
- Fig. 1 is a cross-section view of a compressor head according to a first preferred embodiment of the present invention
- Fig. 2 shows the first embodiment in a double acting arrangement
- Fig. 3 shows the working principles of a self-adjusting chamber-head
- Fig. 4 is an enlarged local view showing diaphragm movements in progress
- Fig. 5 shows a modified version of the first embodiment
- Fig. 6 shows a second embodiment of the invention in a double acting arrangement
- Fig. 7 is an enlarged local view showing piston movements in progress;
- Fig. 8 shows the working principles of a self-adjusting cylinder head;
- Fig. 9 shows the details of a directional bleed hole
- Fig. 10 is an enlarged local view showing a third embodiment of the invention. Detailed Description of Preferred Embodiments
- compressor head for the sake of easy understanding. It should be understood that the same concept could be used for gas, liquid or a mixture of both, and also for a vacuum pump. Therefore, the term “compressor head” should be interpreted as covering “pump head” for all these applications.
- Fig. 1 shows a compressor head 10, which is a diaphragm type machine suitable to high flow applications.
- the compressor head 10 has a housing 40, formed by an end plate 41 and a casing 42 fixed to another casing 52, which is a part of a drive (not shown).
- a piston assembly 20 including a first diaphragm 26, and a chamber-head assembly 30 including a second diaphragm 36.
- the two assemblies define between themselves a working chamber 60.
- the piston assembly 20 includes a piston body 21, which is fixed to and aligned with a free end of a driving shaft 51 by a bolt 22; inlet valves 23 formed by a number of through holes and a flap member secured onto the piston body by an elastomer member 24, which also provides impact protection; and a locking ring 25, which secures the inner edge of the diaphragm 26 to the periphery of the piston body 21.
- the chamber-head assembly 30 includes a head plate 31, which is secured to a leaf spring 34 by a bolt 32; outlet valves 33 formed by a number of through holes and flap members; and a locking ring 35, which secures the inner edge of the diaphragm 36 to the periphery of the head plate 31.
- the diaphragms 26 and 36 are annular in shape with arched cross section, so that they form between them a closely matched complementary relationship.
- the opposing faces of the piston assembly 20 and the chamber-head assembly 30 are shaped to complement each other, leaving minimum dead space between them.
- the working medium comes from the drive side of the piston assembly, as shown by arrows "Flow In", enters the chamber 60 via the inlet valves 23, then passes the outlet valves 33 into the outlet chamber 70 and finally leaves the compressor head via the outlet connector in the centre of the end plate 41, as shown by an arrow "Flow Out".
- the general flow direction is along the piston's pumping direction, so the disturbance to the fluid flow is minimised which ensures high efficiency and low flow noise.
- the areas for fitting inlet and outlet valves are large, flow restriction is reduced. Also, it is convenient to use the inlet flow to cool the drive, if needed.
- the head 10 is a low cost design because the parts can be made of plastics with structures for simple snap fit, making it easy for mass production and assembly.
- Fig. 2 shows a pair of identical heads 10 and 10' fitted to a linear drive 50 in a double acting arrangement.
- the drive can be a linear motor such as that disclosed in our PCT patent application no. WO-99/18649.
- the driving shaft 51 is at its left-hand end position so the chamber 60 in the head 10 at the right-hand side is at its maximum volume, while the chamber at the left-hand side is reduced to virtually zero volume.
- the distance between the front surface of the piston assembly 20 and the opposing surface of the chamber-head assembly 30 is S max , which is the maximum stroke allowable for the drive.
- the chamber-head 30 is fitted inside the casing 42.
- the outer surface of the locking ring 35 and a corresponding inner surface of the casing 42 form a slide bearing/sealing arrangement, which restricts the chamber-head's sideways movement and seals a cushioning chamber 80.
- the chamber-head 30 can move an adjustment distance D adj when there is a pressure difference on its two sides. It works as follows. At its nature status, the chamber-head 30 is biased by the leaf spring 34 towards the casing 42 and set onto a stop edge 43, as shown by the dash line position in Fig. 3. This is the chamber-head's rest position.
- the pressure in the outlet chamber 70 gradually builds up to generate a net total force on the chamber-head 30 against the biasing force by the spring 34 to force the chamber-head away from its rest position by a distance D adj until the net total force is balanced by an increased spring force.
- the adjustment distance D a j can be made proportional to the pressure increase in the outlet chamber 70.
- the cushioning chamber 80 between the diaphragm 36 and the casing 42 has fluid communication with the outlet chamber 70 via one or more one-way valves 45.
- Fig. 4 is an enlarged local view showing the progressive contact between the diaphragms 26 and 36 during operation.
- the solid line position Po shows the piston assembly's end position.
- the piston assembly 20 moves from the end position Po through positions Pj, P 2 and P 3 until it finally touches the chamber-head assembly 30.
- the diaphragm 36 is stiff and capable to maintain its convex surface shape and the diaphragm 26 is bent on top of the diaphragm 36 to form a compliance contact by the force of the linear drive.
- Fig. 5 shows a modified version of the first embodiment, in which the cushion chamber
- the 80 is filled with an elastomer member 81 for impact protection.
- the member 81 is made of an elastic material, such as foamed plastics or rubber, so that it can be easily compressed or released to maintain the convex surface of the diaphragm 36.
- the chamber 80 is sealed by a bellows 38 attached to the locking ring 35, which allows the chamber-head assembly's self- adjusting movement.
- the bellows 38 has one or more directional bleed holes 39 which maintains a high pressure in the chamber 80 during operation but allows slow bleed. Further details of the bleed holes 39 are described with reference to Fig. 9.
- Fig. 6 shows the second embodiment of the present invention, which is basically a piston type compressor head 100 or 100' suitable to high-pressure applications. More particularly, the pair of heads 100 and 100' are fitted to a linear drive 150 in a way similar to that of the first embodiment. Since the two heads are identical, only the one at the right-hand side is fully described here.
- the compressor head 100 has a housing 140 formed by an end cap 141 and a cylinder 142 with a lining 143. Inside the housing 140, there is a piston assembly 120 in the cylinder 142 and a cylinder-head assembly 130 in the end cap 141, defining between them a working chamber 160. On the other side of the cylinder-head assembly 130, there is an outlet chamber 170 for receiving fluid from the chamber 160 via outlet valves 133 and a cushioning chamber 180.
- the piston assembly 120 has a piston core 121, which is fixed to and aligned with a free end of a driving shaft 151 by a bolt 122; a valve plate 123 having inlet valves formed by a number of through holes and a flap member 124; a locking ring 125; a piston diaphragm 126 and a piston sleeve 127.
- the piston diaphragm 126 is secured at its inner edge to the piston core 121 by the valve plate 123, which also serves as a locking ring, and at its outer edge to the piston sleeve 127 by the locking ring 125.
- the inner surface of the piston sleeve 127 and the outer periphery of the piston core 121 form a sliding bearing and a seal is fitted to the outer periphery of the piston core to form a gas tight cushioning chamber 190 inside the piston assembly 120.
- the piston diaphragm 126 has one or more directional bleed holes 129 which allow fluid in the chamber 160 to enter the cushioning chamber 190 easily but restrict flow in the opposite direction. Further description of the bleed holes is made below with reference to Fig. 9.
- the cylinder-head assembly 130 has a head plate 131 biased by a leaf spring 134 away from the piston assembly 120; outlet valves 133 formed by a number of through holes and a flap member; and a locking ring 135, which secures the inner edge of a diaphragm 136 to the periphery of the head plate 131.
- the outer edge of the diaphragm 136 is clamped between the end cap 141 and the cylinder 142 together with its lining 143, which also keep all the parts aligned with the driving shaft 151.
- the diaphragm 136 has a concave face opposing the piston assembly and a number of strengthen ridges on the back surface to maintain the concave shape when there is a higher pressure in the cushioning chamber 180.
- the working principles of the compressor head 100 or 100' and its self-adjusting cylinder head are similar to that in the first embodiment, so they do not need to be repeated here. Only the new features of the second embodiment are explained below.
- Fig. 7 is an enlarged local view showing the piston assembly's movements in compressing phase.
- the solid line position Po is the starting point of the phase. From the position Po to Pi, the piston assembly works in a similar way as a conventional piston.
- the piston assembly reaches the position P 2 , the leading edge of the piston sleeve 127 hits the outer edge of the cylinder-head diaphragm 136 and stops there. After this point, only the piston core 121 moves forward and carries the piston diaphragm 126 towards the cylinder head diaphragm 136, as shown at the position P .
- the piston assembly 120 when the piston assembly 120 reaches the position P , the physical contact between the leading edge of the piston sleeve 127 and the periphery of the diaphragm 136 will form a reliable seal to ensure no leak at the last stage of the compressing phase. The effects of this seal will be further enhanced when the two diaphragms form progressively increased compliance contact. It is also worth mentioning that inside the cushioning chamber 190, the locking ring 125 carries an elastomer member 128, wliich has the effects of forcing the diaphragm 126 to bend outwards to ensure a close contact between the two diaphragms.
- Fig. 8 shows by solid lines the cylinder head's rest position, and by dash lines its position aftef an adjustment distance D adj in response to an outlet pressure increase in the chamber 170. Since the working principles and possible modifications are similar to that in the first embodiment, no further description is necessary.
- Fig. 9 shows the structure details of a bleed hole 39 (129) mentioned in the above two embodiments.
- the hole has one end with a sharp edge and the other end with a smoothly curved edge. Because of the different shapes at two ends, fluid flow in direction A has less flow resistance while that in the opposite direction B has more flow resistance, making its operation with a directional difference.
- Such a bleed hole can be used together with or built into a one-way valve to allow easy flow in one direction and a restricted flow in the opposite direction. Since the use of such bleed holes is known in the art, no more description is needed.
- General Structure of the Third Embodiment Fig. 10 shows a third embodiment of the present invention, which is a modified version of the first embodiment.
- a compressor head 200 has a piston assembly 220 with a diaphragm 226, which is clamped between a chamber-head member 230 and a back support member 240.
- a working chamber 260 is formed between the piston assembly 220 and the chamber-head member 230.
- Both the chamber-head member 230 and the back support member 240 have complementary surface portions for forming progressive compliance contact with the diaphragm 226 during the piston assembly's forward or backward movement.
- the back support member 240 By fitting the back support member 240, the total surface area exposed to backpressure is reduced progressively during the piston assembly's backward movement from position P 3 to position Po, making it easier to achieve a longer stroke.
- This arrangement would be particularly suitable to a vacuum pump application, in which a longer stroke would help to generate a higher vacuum in the chamber 260.
- the compressor head according to the present invention has at least the following advantages, a) Low manufacturing costs because most of the parts can be made of plastics or rubber and can be assembled by simple snap fit. b) High efficiency over a wide operation range. c) High compression ratio and/or flow rate by a relatively small stroke. d) Lubricant-free, leak-free and maintenance-free operation. e) Low noise and vibration.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Reciprocating Pumps (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB0505348A GB2409007B (en) | 2002-11-13 | 2003-11-03 | Compressor head |
AU2003278381A AU2003278381A1 (en) | 2002-11-13 | 2003-11-03 | Compressor head |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB0226440.6 | 2002-11-13 | ||
GB0226440A GB2395237A (en) | 2002-11-13 | 2002-11-13 | Compressor head |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2004044423A1 true WO2004044423A1 (en) | 2004-05-27 |
Family
ID=9947720
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/GB2003/004699 WO2004044423A1 (en) | 2002-11-13 | 2003-11-03 | Compressor head |
Country Status (4)
Country | Link |
---|---|
CN (1) | CN1711419A (en) |
AU (1) | AU2003278381A1 (en) |
GB (2) | GB2395237A (en) |
WO (1) | WO2004044423A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN101356371B (en) * | 2005-11-14 | 2011-09-14 | 泽维技术公司 | Membrane pump |
EP2418385A1 (en) * | 2010-03-30 | 2012-02-15 | Safety-Kleen Europe Limited | Diaphragm pump |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102011003461A1 (en) | 2011-02-01 | 2012-08-02 | Robert Bosch Gmbh | Diaphragm pump and exhaust aftertreatment system with a diaphragm pump |
DE102013015055B4 (en) * | 2013-09-12 | 2019-04-25 | Eta Opt Gmbh | Suction lifting device for manipulating objects in z. B. Workshops with two alternately expanatory bellows |
CN105114297B (en) * | 2015-09-10 | 2018-02-16 | 珠海格力电器股份有限公司 | Sealing structure of diaphragm pump head cover |
CN105604922A (en) * | 2016-01-27 | 2016-05-25 | 北京天高隔膜压缩机有限公司 | Diaphragm compressor suitable for recycling waste steam |
CN111016434B (en) * | 2019-12-25 | 2021-07-27 | 西安交通大学 | Thin film type ink-jet printing head based on extrusion mode |
US11873802B2 (en) * | 2020-05-18 | 2024-01-16 | Graco Minnesota Inc. | Pump having multi-stage gas compression |
CN114810562B (en) * | 2022-05-10 | 2024-02-27 | 浙江永球科技有限公司 | Diaphragm vacuum pump |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2463766A (en) * | 1944-01-05 | 1949-03-08 | Dapco Products Inc | Compressor |
GB1210065A (en) * | 1967-03-31 | 1970-10-28 | I V Pressure Controllers Ltd | Improvements in or relating to diaphragms |
US3936245A (en) * | 1972-04-03 | 1976-02-03 | Johnson Service Company | Fluid compressing apparatus |
US4594058A (en) * | 1984-06-01 | 1986-06-10 | The Johns Hopkins University | Single valve diaphragm pump with decreased sensitivity to ambient conditions |
US4666378A (en) * | 1984-04-25 | 1987-05-19 | Mitsubishi Denki Kabushiki Kaisha | Diaphragm type pump device having a cushion member |
US5551843A (en) * | 1993-11-09 | 1996-09-03 | Knf Neuberger Gmbh | Pump with a driving motor and a case |
DE19910920A1 (en) * | 1999-03-12 | 2000-09-14 | Asf Thomas Ind Gmbh & Co Kg | Membrane pump, in particular, micromembrane pump with oscillating armature comprises oscillating armature guide element which is produced together with surrounding plastic injection molding |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1239162A (en) * | 1968-07-17 | 1971-07-14 | ||
US3936345A (en) * | 1971-06-11 | 1976-02-03 | Bielomatik Leuze & Co. | Apparatus for welding flexible members into a frame |
GB1418993A (en) * | 1972-03-08 | 1975-12-24 | Becker E | Diaphragm pump particularly for the generation of vacuum |
GB9310786D0 (en) * | 1993-05-25 | 1993-07-14 | Walker Ian R | Circulation pump for high purity gases at high pressures |
-
2002
- 2002-11-13 GB GB0226440A patent/GB2395237A/en not_active Withdrawn
-
2003
- 2003-11-03 CN CNA2003801031685A patent/CN1711419A/en active Pending
- 2003-11-03 WO PCT/GB2003/004699 patent/WO2004044423A1/en not_active Application Discontinuation
- 2003-11-03 AU AU2003278381A patent/AU2003278381A1/en not_active Abandoned
- 2003-11-03 GB GB0505348A patent/GB2409007B/en not_active Expired - Fee Related
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2463766A (en) * | 1944-01-05 | 1949-03-08 | Dapco Products Inc | Compressor |
GB1210065A (en) * | 1967-03-31 | 1970-10-28 | I V Pressure Controllers Ltd | Improvements in or relating to diaphragms |
US3936245A (en) * | 1972-04-03 | 1976-02-03 | Johnson Service Company | Fluid compressing apparatus |
US4666378A (en) * | 1984-04-25 | 1987-05-19 | Mitsubishi Denki Kabushiki Kaisha | Diaphragm type pump device having a cushion member |
US4594058A (en) * | 1984-06-01 | 1986-06-10 | The Johns Hopkins University | Single valve diaphragm pump with decreased sensitivity to ambient conditions |
US5551843A (en) * | 1993-11-09 | 1996-09-03 | Knf Neuberger Gmbh | Pump with a driving motor and a case |
DE19910920A1 (en) * | 1999-03-12 | 2000-09-14 | Asf Thomas Ind Gmbh & Co Kg | Membrane pump, in particular, micromembrane pump with oscillating armature comprises oscillating armature guide element which is produced together with surrounding plastic injection molding |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN101356371B (en) * | 2005-11-14 | 2011-09-14 | 泽维技术公司 | Membrane pump |
EP2418385A1 (en) * | 2010-03-30 | 2012-02-15 | Safety-Kleen Europe Limited | Diaphragm pump |
Also Published As
Publication number | Publication date |
---|---|
CN1711419A (en) | 2005-12-21 |
GB2395237A (en) | 2004-05-19 |
GB0505348D0 (en) | 2005-04-20 |
GB2409007A (en) | 2005-06-15 |
AU2003278381A1 (en) | 2004-06-03 |
GB0226440D0 (en) | 2002-12-18 |
GB2409007B (en) | 2005-12-21 |
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