US20020176791A1 - Leakproof pump for use in an inking mechanism of a rotary printing press - Google Patents

Leakproof pump for use in an inking mechanism of a rotary printing press Download PDF

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Publication number
US20020176791A1
US20020176791A1 US10/121,605 US12160502A US2002176791A1 US 20020176791 A1 US20020176791 A1 US 20020176791A1 US 12160502 A US12160502 A US 12160502A US 2002176791 A1 US2002176791 A1 US 2002176791A1
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US
United States
Prior art keywords
piston
cylinder
pump
bore
pump body
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US10/121,605
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English (en)
Inventor
Yoshinori Uera
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Tokyo Kikai Seisakusho Co Ltd
Original Assignee
Tokyo Kikai Seisakusho Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Tokyo Kikai Seisakusho Co Ltd filed Critical Tokyo Kikai Seisakusho Co Ltd
Assigned to KABUSHIKI KAISHA TOKYO KIKAI SEISAKUSHO reassignment KABUSHIKI KAISHA TOKYO KIKAI SEISAKUSHO ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: UERA, YOSHINORI
Publication of US20020176791A1 publication Critical patent/US20020176791A1/en
Abandoned legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F31/00—Inking arrangements or devices
    • B41F31/02—Ducts, containers, supply or metering devices
    • B41F31/08—Ducts, containers, supply or metering devices with ink ejecting means, e.g. pumps, nozzles

Definitions

  • This invention relates generally to pumps and particularly to a pump that is best suited for use in inking mechanisms of rotary printing presses as typified by those of the offset lithographic variety. More particularly, the invention pertains to a pump of the kind having a motor-driven piston that concurrently undergoes linear, relatively short-stroke reciprocation and rotation for metering ink toward the plate cylinder of the press.
  • One end of the cylinder is pressure-tightly closed, and the piston projects through the other end of the cylinder for connection to a variable speed drive motor via a drive linkage including a crank.
  • the axis of the drive motor is at an angle to that of the cylinder, and the drive linkage connects the motor output shaft to the piston in such a manner that the piston not only rotates but reciprocates linearly in response to the rotation of the drive motor.
  • the piston makes one complete revolution and one complete reciprocation with each complete revolution of the drive motor.
  • the piston blocks both suction and discharge ports in dead-center positions at both extremities of its linear travel and places the cylinder bore in communication with the suction port during its travel in one direction and in communication with the discharge port during its travel in the other direction.
  • the piston completes one suction stroke and one delivery stroke during each complete revolution thereof, supplying the ink toward the plate cylinder by well metered quantities.
  • Another object of the invention is to make the most of the preexisting parts of the pump in making the same leakproof.
  • Still another object of the invention is to seal the pump against leakage in a manner permitting easy mounting, dismounting, and maintenancing of the sealing means.
  • the present invention may be summarized as a pump capable of metering a fluid such as printing ink, comprising pump body means defining a bore which is pressure-tightly closed at a first end thereof, together with a suction port and a discharge port which are both open to the bore in preassigned different angular positions thereon.
  • a piston Slidably received in the bore in the pump body means, a piston has one end projecting from a second end of the bore for connection to a drive motor via a drive linkage such that the piston undergoes joint rotation and linear reciprocation in response to motor rotation.
  • an end seal means sealing the second end of the bore against the leakage of the fluid from between the pump body means and the piston.
  • the bore is defined by a cylinder, or cylindrical vessel, mounted fast to a pump body, and the end seal means comprises a sealing ring received in a bore enlargement formed in the cylinder at the second end of the bore, and a retainer ring engaged in the bore enlargement for retaining the sealing ring in fluid-tight contact with both the piston and the cylinder.
  • the end seal means comprises a sealing ring surrounding the piston and held against the end of the cylinder, and a mounting ring screw-threadedly engaged with the cylinder for retaining the sealing ring in position.
  • the bore is defined directly in the pump body, and the end seal means comprises a sealing ring surrounding the piston and held against the pump body, and a mounting ring surrounding the piston and fastened to the pump body for retaining the sealing ring in position.
  • the sealing ring has a pair of annular, concentric lips formed thereon.
  • the lipped sealing rings are sufficiently elastic radially thereof that the piston and pump body, or piston and cylinder, need not be machined to no such stringent dimensional tolerances as have been required heretofore.
  • the dimensional difference between the two mating parts can be greater, either at the time of manufacture or as a result of wear in use, without the fear of leakage.
  • FIG. 1 is a plan view of a typical inking pump arrangement for an offset printing press, comprising eight pump units each constructed according to the novel concepts of the invention
  • FIG. 2 is an enlarged vertical section taken along the line II-II in FIG. 1 and showing the construction of each pump unit in detail;
  • FIG. 3 is a still more enlarged, fragmentary vertical section through the FIG. 2 pump unit, showing in particular the sealing means according to the invention
  • FIG. 4 is a view similar to FIG. 2 but showing an alternative embodiment of the invention.
  • FIG. 5 is a view similar to FIG. 3 but showing the sealing means of the FIG. 4 embodiment
  • FIG. 6 is a view similar to FIG. 2 but showing another alternative embodiment of the invention.
  • FIG. 7 is a view similar to FIG. 3 but showing the sealing means of the FIG. 6 embodiment.
  • FIG. 1 a typical inking pump arrangement A for an offset printing press.
  • the pump arrangement A incorporates any required number of, eight shown by way of example, pump units P of like design which are arranged side by side in a transverse direction of the web of paper, not shown, traveling along a predefined path in the press.
  • This invention particularly concerns the construction of each pump unit P. Since all the pump units P are alike in construction, only one of them will be described in detail with reference to FIGS. 2 and 3, FIG. 2 being taken along the line II-II in FIG. 1, with the understanding that the same description applies to all the other pump units.
  • the representative pump unit P has a pump body 1 which is common to all the individual pump units.
  • the pump body 1 is a one-piece construction of a relatively thick front part 1 a , shown directed to the left, and a thin rear part 1 b , which are opposed to each other across a hollow 16 .
  • the front part 1 a of the pump body 1 will be hereinafter referred to as the front body part, and the rear part 1 b as the rear body part.
  • a cover plate 1 c which also is common to all the pump units P, openably closes the top of the hollow 16 .
  • a hollow, angled cylinder, or cylindrical vessel, 2 defining a bore 20 .
  • a piston 3 is slidably but pressure-tightly mounted in the bore 20 for both rectilinear reciprocation and angular motion.
  • One end of the bore 20 is pressure-tightly closed by a plug 23 whereas the other end thereof is open to permit the piston 3 to project into the hollow 16 .
  • the piston end thus projecting into the hollow 16 is operatively coupled, in a manner yet to be detailed, to a variable speed drive motor 4 which is mounted fast to the rear body part 1 b.
  • the cylinder 2 has an ink suction port 21 and an ink discharge port 22 formed in diametrically opposite positions and in axial alignment with each other for the ingress and egress, respectively, of ink into and out of the cylinder bore 20 .
  • the suction port 21 communicates with an ink reservoir, not shown, via a system of conduits 14 , and the discharge port 22 with the familiar ink rail, not shown, of the press via another system of conduits 15 .
  • the piston 3 has a recess 31 extending rearwardly from its front end 30 to a relatively short extent. The recess 31 is of such depth (i.e.
  • the piston 3 is capable of opening only either of the suction port 21 and discharge port 22 to the cylinder bore 20 at one time.
  • the suction port 21 and discharge port 22 are therefore alternately placed in communication with the cylinder bore 20 at each half revolution of the piston 3 , and both out of communication therewith in the other angular positions of the piston.
  • the drive motor 4 has a drive shaft 40 projecting into the hollow 16 .
  • the drive motor 4 is so angled in relation to the cylinder 2 that the axis CL 1 of the drive shaft 40 crosses the axis CL 2 of the piston 3 at an angle ⁇ .
  • a preferred example of the drive motor 4 is a known stepper motor capable of rotation by discrete increments in response to stepping pulses. It is also preferred that the drive motor 4 be so controlled as to rotate through a prescribed angle of, say, forty-five degrees in response to each series of stepping pulses, standing still pending the arrival of the next series of such pulses.
  • the reference numeral 5 generally denotes a drive linkage connecting the drive shaft 40 to the piston 3 so as to cause both rotation and linear reciprocation of the piston in response to the rotation of the drive shaft.
  • the drive linkage 5 comprises an overhung crank 50 mounted fast to the drive shaft 40 for joint rotation therewith, and a connecting pin 51 connecting the crank to the piston 3 .
  • the crank 50 is composed of a crank base portion 50 a proximally fastened to the drive shaft 40 , and a crank arm 50 b extending forwardly from the distal end of the crank base portion in parallel relationship to the drive shaft and, in consequence, nonparallel relationship to the piston 3 .
  • the crank arm 50 b revolves around the exposed rear end portion of the piston 3 with the incremental rotation of the drive shaft 40 .
  • the connecting pin 51 of the drive linkage 5 is fastened at one end to the piston 3 , with the axis CL 3 of the pin crossing the axis CL 2 of the piston at a prescribed angle which is ninety degrees in this particular embodiment.
  • the other end of the connecting pin 51 slidably extends through a spherical bearing 52 mounted to the crank arm 50 b .
  • the spherical bearing 52 permits variation in the angular attitude of the connecting pin 51 relative to the crank arm 50 b with the rotation of the drive motor 4 , with the consequent combined rotation and linear reciprocation of the piston in response to the rotation of the crank arm.
  • the angle between connecting pin axis CL 3 and drive shaft axis CL 1 is subject to change with motor rotation.
  • the angular position of the recess 31 on the piston 3 must be predetermined in relation to the angular relationship between the axes CL 1 and CL 3 .
  • the angle between drive shaft axis CL 1 and connecting pin axis CL 3 maximizes at ⁇ at the end of the suction stroke of the piston 3 and minimizes at ⁇ at the end of the discharge stroke of the piston.
  • the piston 3 makes one complete revolution and one complete reciprocation with each complete revolution of the drive motor 4 .
  • the recess 30 is so angularly positioned on the piston 3 that both suction port 21 and discharge port 22 are closed when the piston is in dead-center positions at both extremities of its stroke. Further the piston 3 places the suction port 21 in communication with the cylinder bore 20 during its suction stroke, which is to the right as viewed in FIG. 2, and places the discharge port 22 in communication with the cylinder bore 20 during its discharge stroke.
  • a cylinder end seal 6 is provided at the rear end of the cylinder 2 in order to prevent leakage of the ink from between the cylinder and the piston 3 .
  • the cylinder bore 20 is enlarged at its end open to the hollow 16 , FIG. 2, in the pump body 1 .
  • a sealing ring 71 complete with a pair of annular lips 74 , is snugly received in this cylinder bore enlargement 20 a so as to concentrically surround the piston 3 . Both formed on one side surface of the sealing ring 71 , the annular lips 74 are spaced from each other radially of the sealing ring.
  • a wear-resisting synthetic rubber is a preferred material of the sealing ring 71 complete with the lips 74 .
  • the sealing ring 71 is positively retained in position in the cylinder bore enlargement 20 a by a retainer ring 73 via a washer 72 . Both washer 72 and retainer ring 73 are shown engaged in the cylinder bore enlargement 20 a .
  • the sealing ring 71 makes fluid-tight contact with the surfaces of the cylinder 2 and piston 3 .
  • the annular lips 74 of the sealing ring 71 extend therefrom in a direction away from the exposed rear end of the piston 3 in order to even more effectively oppose ink flow in the leaking direction.
  • the cylinder end seal 6 of this particular embodiment is compactly mounted in the enlargement 20 a of the cylinder bore 20 .
  • This sealing design is intended for the ease with which the prior art ink pumps of this type may be reconstructed for freedom from ink leakage, all that is required to attain this objective according to the teachings of the instant invention being the modification of the internal configuration of the cylinder 2 and the provision of the sealing ring 71 , washer 72 and retainer ring 73 .
  • the cylinder bore 20 is conventionally pressure-tightly closed at its front end by the plug 23 but is open at its rear end, permitting the piston 13 to project into the hollow 16 in the pump body 1 for coupling to the drive motor shaft 40 .
  • the present invention specifically concerns how to most effectively and economically seal the rear end of the bore 20 against the leakage of the printing ink.
  • the piston 3 is on its suction stroke when the suction port 21 is in communication with the bore 20 , and on its delivery stroke when the discharge port 22 is in communication with the bore.
  • the piston 3 will retreat into the hollow 16 in the pump body 1 on its suction stroke, drawing the ink into the cylinder bore 20 through the suction port 21 , and advance deeper into the cylinder bore on its delivery stroke, forcing the ink out through the discharge port 22 .
  • the cylinder end seal 6 of FIG. 3 is well calculated to prevent ink leakage from the rear end of the cylinder 2 .
  • the cylinder end seal 6 features the sealing ring 71 installed between cylinder 2 and piston 3 , with the pair of annular lips 74 oriented forwardly therefrom, and firmly retained in position by the retainer ring 73 via the washer 72 .
  • the lipped sealing ring 71 will block the passage of the ink between cylinder 2 and piston 3 , scraping the ink off the surface of the piston as the latter both rotates and linearly reciprocates in sliding contact therewith.
  • the sealing ring 71 will serve its intended purposes for a prolonged period of time in the face of possible wear of the piston. It is also possible to provide sufficient clearance between cylinder 2 and piston 3 to preclude the difficulties and inconveniences that might arise from solid particles contained in the ink. All in all, each pump unit P, and of course the complete pump arrangement A will be much more extended in useful life than in the absence, as has been the case heretofore, of the cylinder end seal 6 . It will unnecessary, moreover, to make the contacting surfaces of the cylinder 2 and piston 3 as hard as when, also as has been the case heretofore, they had a minimum clearance therebetween to avoid ink leakage.
  • FIG. 4 shows another preferred form of pump unit P a according to this invention, for use in the inking pump arrangement A of FIG. 1 in substitution for each pump unit P.
  • FIGS. 2 and 4 A comparison of FIGS. 2 and 4 will reveal that the FIG. 4 pump unit P a differs from its FIG. 2 counterpart P only in the constructions of its cylinder end seal 6 a and some associated parts of the pump body 1 and cylinder 2 . Only this alternative end seal 6 a , as well as the correspondingly modified parts of the pump body 1 and cylinder 2 , will therefore be discussed in detail with reference directed mostly to FIG. 5, an enlargement of the alternative end seal.
  • the alternative cylinder end seal 6 a includes a sealing ring 81 , similar in both construction and material to the sealing ring 71 of the FIG. 3 seal 6 , which is fitted over the piston 3 and which is held against the rear end 26 of the cylinder 2 .
  • the sealing ring 81 is firmly retained in position by a mounting ring 82 concentrically surrounding the cylinder 2 and piston 3 .
  • the cylinder 2 is formed to include a reduced diameter end portion 24 which is partly screw threaded at 25 .
  • the mounting ring 82 has a stepped bore composed of, from its rear end forwardly, a first portion 82 a of smallest diameter through which the piston 3 extends with clearance, a second portion 83 of greater diameter accommodating the sealing ring 81 , a third portion 84 of still greater diameter in sliding fit with the reduced diameter portion 24 of the cylinder 2 , and a fourth portion 85 of approximately the same diameter as the third portion 84 which has an internal screw thread cut therein to mesh with the external thread 25 on the cylinder 2 .
  • the third bore portion 84 has an annular groove 86 cut therein to receive an O-ring seal 88 .
  • the sealing ring 81 can be mounted in position between cylinder 2 and piston 3 simply as the mounting ring 82 , together with the sealing ring received in its second bore portion 83 , is placed around the piston and turned over the reduced diameter end portion of the cylinder for threaded engagement therewith.
  • the mounting ring 82 can be axially positioned with respect to the cylinder 2 simply by turning the ring until the shoulder 87 between its bore portions 83 and 84 comes into abutment against the rear end 26 of the cylinder.
  • the lipped sealing ring 81 will make leakproof engagement with the confronting surfaces of the piston 3 and the mounting ring 82 .
  • the O-ring seal 88 will seal the joint between cylinder 2 and mounting ring 82 , making it impervious to the ink.
  • FIG. 5 At 89 in FIG. 5 are seen two or more tool holes bored in the mounting ring 82 at circumferential spacings. A suitable tool, not shown, is to be inserted in any of these holes 89 for turning the mounting ring 82 into and out of threaded engagement with the cylinder 2 .
  • FIG. 6 pump unit P b differs from its FIG. 2 counterpart P primarily in that the piston 3 is mounted in a bore 10 of cylindrical shape that is cut directly in the front part 1 a of the pump body 1 .
  • the pump body 1 here should therefore be construed to serve the additional purpose of the cylinder 2 of the foregoing embodiments.
  • the cylinder end seal 6 b of this pump unit P b is modified accordingly.
  • the pump body front part 1 a has formed in its rear surface a relatively shallow bore 17 concentric with the cylinder bore 10 , and another, similarly shallow bore 18 of reduced diameter cut centrally in the bottom of the bore 17 , with an annular shoulder 19 between the bores 17 and 18 .
  • the modified cylinder end seal 6 b features a sealing ring 91 , similar in both construction and material to the sealing ring 71 of the FIG. 3 cylinder end seal 6 , which is fitted over the piston 3 and which is held against the bottom of the smaller diameter bore 18 in the pump body front part 1 a.
  • a mounting ring 92 which is received in the larger diameter bore 17 in the pump body front part 1 a and which loosely surrounds the piston 3 .
  • the mounting ring 92 is fastened to the pump body front part 1 a with a plurality of, one seen, screws 98 .
  • the mounting ring 92 is formed to include a boss 94 projecting concentrically therefrom to be received in the smaller diameter bore 18 in the pump body front part 1 a .
  • the boss 94 is hollow, defining a space 93 for accommodating the sealing ring 91 in fluid-tight contact with the piston 3 .
  • the sealing ring 91 functions mostly to seal the joint between piston 3 and mounting ring 92 .
  • the mounting ring 92 has formed therein an annular groove 96 to receive part of an O-ring seal 97 which is held against the shoulder 19 between the bores 17 and 18 in the pump body front part 1 a , sealing the joint between the pump body and the mounting ring 92 . Thus is prevented the leakage of ink from between piston and pump body.
  • cylinder end seals 6 , 6 a and 6 b offer numerous and substantive advantages despite their simplicity of construction. They will be effective, preventing ink leakage and making it unnecessary to clean the pump units or units at regular intervals, even if the clearance between piston and cylinder is intentionally made greater than heretofore or becomes greater with the lapse of time.
  • the cylinder 2 , or piston body 1 , and the piston 3 need not be machined so close tolerances as heretofore since the clearance therebetween can be made greater without the fear of ink leakage.
  • the lipped sealing rings 71 , 81 or 91 are sufficiently elastic radially of the piston 30 to stay in fluid-tight contact with the pertinent members in the face of such greater clearances.
  • the contacting surfaces of the cylinder 2 , or pump body 1 , and piston 3 need not be so hard as to resist wear for any prolonged period of time because the end seals 6 , 6 a or 6 b will maintain their sealing functions even if the contacting surfaces are worn to a certain extent.
  • the pump will stay leakproof and operable for an extended period of time as the wear of the contacting surfaces of the mating members of the piston in use is taken up by the annular lips, in particular, of the sealing rings.
  • FIGS. 5 and 7 The cylinder end seals of FIGS. 5 and 7 in particular are designed for ease of disassembly for maintenance and repair.

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  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Inking, Control Or Cleaning Of Printing Machines (AREA)
US10/121,605 2001-05-23 2002-04-15 Leakproof pump for use in an inking mechanism of a rotary printing press Abandoned US20020176791A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2001153553A JP2002349424A (ja) 2001-05-23 2001-05-23 印刷機用ポンプ
JPP2001-153553 2001-05-23

Publications (1)

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US20020176791A1 true US20020176791A1 (en) 2002-11-28

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ID=18998054

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US10/121,605 Abandoned US20020176791A1 (en) 2001-05-23 2002-04-15 Leakproof pump for use in an inking mechanism of a rotary printing press

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US (1) US20020176791A1 (ja)
EP (1) EP1260366B1 (ja)
JP (1) JP2002349424A (ja)
DE (1) DE60224750T2 (ja)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7785084B1 (en) * 2004-09-16 2010-08-31 Fluid Metering, Inc. Method and apparatus for elimination of gases in pump feed/injection equipment
US8562310B1 (en) 2004-09-16 2013-10-22 Fluid Metering, Inc. Chlorination system with corrosion minimizing components
US9261085B2 (en) 2011-06-10 2016-02-16 Fluid Metering, Inc. Fluid pump having liquid reservoir and modified pressure relief slot
CN109927407A (zh) * 2019-03-05 2019-06-25 杭州科雷机电工业有限公司 一种注射式供墨泵

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4484139B2 (ja) 2004-03-09 2010-06-16 株式会社東京機械製作所 印刷機用インキポンプ装置
CN114934822B (zh) * 2022-05-24 2023-08-18 安庆船用电器有限责任公司 一种船用发电机组用滑油预供泵

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3013830A (en) * 1958-06-27 1961-12-19 Garlock Inc Packing
US3062555A (en) * 1960-05-11 1962-11-06 Hydromatics Inc Packed joint
US3394939A (en) * 1966-12-08 1968-07-30 Johns Manville Fluid pressure actuable seal
US3765690A (en) * 1971-01-21 1973-10-16 Ato Inc Composite seal
US4601235A (en) * 1984-06-18 1986-07-22 Trw Inc. Reciprocating pump piston
US4708605A (en) * 1985-06-05 1987-11-24 Franz Orlita Piston pump with rotating piston having a universal joint
US5074767A (en) * 1990-10-24 1991-12-24 Hypro Corporation Positive displacement pump with rotating reciprocating piston and improved lubrication feature
US5513858A (en) * 1994-04-26 1996-05-07 A. W. Chesterton Company Split interlocking seal

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE226560C (ja) *
EP0298140A1 (de) * 1987-07-06 1989-01-11 Dozsa Mezögazdasagi Termelöszövetketzet Dosierpumpe mit einem Drehkolben
US5246354A (en) * 1991-01-31 1993-09-21 Abbott Laboratories Valveless metering pump with reciprocating, rotating piston
JP2864447B2 (ja) * 1994-05-31 1999-03-03 株式会社東京機械製作所 印刷機用ポンプ
JP3095744B1 (ja) * 1999-08-27 2000-10-10 株式会社東京機械製作所 印刷機用ポンプ

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3013830A (en) * 1958-06-27 1961-12-19 Garlock Inc Packing
US3062555A (en) * 1960-05-11 1962-11-06 Hydromatics Inc Packed joint
US3394939A (en) * 1966-12-08 1968-07-30 Johns Manville Fluid pressure actuable seal
US3765690A (en) * 1971-01-21 1973-10-16 Ato Inc Composite seal
US4601235A (en) * 1984-06-18 1986-07-22 Trw Inc. Reciprocating pump piston
US4708605A (en) * 1985-06-05 1987-11-24 Franz Orlita Piston pump with rotating piston having a universal joint
US5074767A (en) * 1990-10-24 1991-12-24 Hypro Corporation Positive displacement pump with rotating reciprocating piston and improved lubrication feature
US5513858A (en) * 1994-04-26 1996-05-07 A. W. Chesterton Company Split interlocking seal

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7785084B1 (en) * 2004-09-16 2010-08-31 Fluid Metering, Inc. Method and apparatus for elimination of gases in pump feed/injection equipment
US8562310B1 (en) 2004-09-16 2013-10-22 Fluid Metering, Inc. Chlorination system with corrosion minimizing components
US9964101B2 (en) 2004-09-16 2018-05-08 Fluid Metering, Inc. Adjustable pumping apparatus
US9261085B2 (en) 2011-06-10 2016-02-16 Fluid Metering, Inc. Fluid pump having liquid reservoir and modified pressure relief slot
US9828978B2 (en) 2011-06-10 2017-11-28 Fluid Metering, Inc. Fluid pump having liquid reservoir and modified pressure relief slot
CN109927407A (zh) * 2019-03-05 2019-06-25 杭州科雷机电工业有限公司 一种注射式供墨泵

Also Published As

Publication number Publication date
EP1260366B1 (en) 2008-01-23
JP2002349424A (ja) 2002-12-04
DE60224750D1 (de) 2008-03-13
DE60224750T2 (de) 2009-01-22
EP1260366A1 (en) 2002-11-27

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AS Assignment

Owner name: KABUSHIKI KAISHA TOKYO KIKAI SEISAKUSHO, JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:UERA, YOSHINORI;REEL/FRAME:012806/0347

Effective date: 20020304

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION