US3534663A - Ink injector pump output control mechanism - Google Patents

Ink injector pump output control mechanism Download PDF

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Publication number
US3534663A
US3534663A US773392A US3534663DA US3534663A US 3534663 A US3534663 A US 3534663A US 773392 A US773392 A US 773392A US 3534663D A US3534663D A US 3534663DA US 3534663 A US3534663 A US 3534663A
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United States
Prior art keywords
pump
control member
ink
spring
adjustment
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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.)
Expired - Lifetime
Application number
US773392A
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English (en)
Inventor
Frank J Doyle
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.)
Miehle Goss Dexter Inc
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Miehle Goss Dexter Inc
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Publication date
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Publication of US3534663A publication Critical patent/US3534663A/en
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Expired - Lifetime legal-status Critical Current

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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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2064—Housings
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2035—Cylinder barrels
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/22—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/007—Installations or systems with two or more pumps or pump cylinders, wherein the flow-path through the stages can be changed, e.g. from series to parallel

Definitions

  • a control mechanism and method of operation for a positive displacement ink injector pump is disclosed in which resiliently separable linkage connections enable displacement adjustments to be applied to the system while the pump displacement mechanism is stationary and immobilized due to fluid entrapped within the pumping chambers, and in which the adjustment is thereafter effected when the pump is again stated.
  • the present invention relates to displacement control mechanisms for positive displacement pumps, and in its principal aspect relates to multiple-piston rotary swash plate type pumps in which displacement adjustments are applied while the pump is stationary as well as when it is in operation.
  • Rotary positive displacement pumps utilizing swash plate output adjustment means have been known and used for some time.
  • One useful application of such pumps has been in ink supply systems for newspaper printing press units in which each portion of the width of a printed page may require a different amount of ink in order to maintain the proper scale of color"or ink intensity for that portion of the page.
  • a separate positive displacement ink pump with variable displacement means is used for each column area of page width so that each pump may be individually adjusted to correct the color or intensity of the corresponding portion of the printed page.
  • swash plate type output control mechanisms are prone to lock up and become immovable due to entrapped ink when the pump is stopped. Thus, no change in displacement can be made when the press unit is not in operation, and any such changes must await restarting of the press so that the entrapped ink may be purged or flushed from the system. This is often the cause of considerable inconvenience when it is desired to change from black to colored ink, for example, or when it is desired to turn off or silence" a page section of the ink pump system after a press run.
  • Another object is to provide an operating mechanism of the above type that is simple and inexpensive to build and maintain, and which will hold operating adjustments firmly and accurately.
  • a further object is to provide a positive displacement ink pump which may be quickly and efficiently purged of ink during cleaning or changeover to another color of ink through a simple adjustment of its operating mechanism.
  • FIG. 1 is a plan view in section of a portion of an ink pump assembly exemplifying the present invention, showing two individual ink pump units;
  • FIG. 2 is a section taken in the plane 2-2 of FIG. 1;
  • FIG, 3 is a section taken in the plane 3-3 of FIG. 2;
  • FIG. 4 is a section similar to FIG. 3, with the pump barrel rotated 90 on its rotational axis;
  • FIG. 5 is a partial perspective of the main operating elements of the mechanism of the previous FIGS., with portions of the assembly frame being deleted for clarity;
  • FIG. 6 is an enlarged partial section of the cam and intermediate member shown in FIG. 4;
  • FIG. 7 is a partial view similar to FIG. 6 illustrating the various members in an alternate operational position
  • FIG. 8 is a partial perspective of a second operating mechanism exemplifying the present invention, with portions of assembly being deleted for clarity;
  • FIG. 9 is an enlarged plan view of the intermediate and adjustment members of the mechanism of FIG. 8, taken in the plane 9-9;
  • FIG. 10 is an elevation taken in the plane 10-10 of FIG. 9;
  • FIG. 11 is a partial perspective of a third operating mechanism exemplifying the present invention, with portions of the assembly being deleted for clarity;
  • FIG. 12 is an enlarged plan view of the operating member of FIG. 11, taken in the plane 12-12;
  • FIG. 13 is an elevation taken in the plane 13-13 of FIG. 12, with additional associated mechanism being illustrated.
  • FIG. I there is shown a fragmentary portion of a first exemplary ink pump assembly frame I0 containing two individual ink pump units 11.
  • Each ink pump unit I] consists of a cylindrical pump barrel I2 journaled for rotation about a stub shaft 13 fixed to the frame 10.
  • Gears 15 are affixed to one end of each of the pump barrels I2, and intermesh as a linear train which is driven from a drive gear (not shown) powered from the press drive.
  • Ink is received by each individual pump unit 11 from a common inlet channel I6 formed as a bore in the frame 10.
  • An annular groove 17 cut in the stub shaft 13 intersects the inlet channel 16 and directs ink into an inlet bore 18 within the base section of the stub shaft 13 that is closed by a plug 19.
  • Also within the base section is an ink discharge bore 20 which communicates with a fitting 21 leading to the particular column area of the printed page which that particular pump unit 11 is to supply.
  • An inlet port 22 and an outlet port 23 are disposed from one another and communicate with the inlet bore 18 and outlet bore 20, respectively.
  • the rotating pump barrel 12 contains a plurality ofpumping chambers, 25, each being formed as a cylinder in which a piston 26 reciprocates.
  • Each pumping chamber 25 alternately communicates with the inlet and outlet bores 18, 20 by way of transfer ports 27.
  • a bearing 28 made of solid antifriction material takes thrust forces from the barrel l2 and also acts as a seal, bearing against a like member 29 which is pinned to the frame 10.
  • a tiltable swash plate means including a pivoted control member 31 pivoted on shafts 30 and having a control pin 32 protruding through an opening at the rear of the frame 10.
  • the control member 31 includes a rotatable spider 33 mounted in a double row ball bearing 35 for rotation with respect to the control member 31. Attached to each end of the spider 33 is a chain link 36 which is joined at its opposite end to a piston 26.
  • Thrust force to keep the pump barrel I2 urged against the bearing 29 is furnished by a compression spring 37 which is received at one end within a central socket in the pump barrel I2, and includes a thrust button 38 at the other end which mates with a hemispherical surface formed on the end of the spider 33.
  • the control member 31 may swing about its pivot shafts 30 without shifting the position of the thrust button 38 in relation to the pump barrel 12, or varying the amount of thrust force tending to seat the pump barrel 12 on the bearings 28, 29.
  • an improved operating linkage is provided for the control member 31 of each pump unit 11 in which the delivery stroke of the pistons 26 may be varied directly during pump operation, or as a preset adjustment when the pump is still, even though entrapped ink within one or more pumping chambers 25 causes the pistons 26 to be immobilized. It will be understood that such a frozen pump condition also rigidly locks the control member 31 against rotation about its pivot axis, causing the control pin 32 to be likewise locked in place.
  • each pump unit 11 has a separable linkage which transmits adjustment motion from an adjustment cam 42, and resilient means are employed for connectively biasing the separable linkage in a manner which allows the position to which the member 31 will move as soon as it is freed when the pump unit 11 is restarted to be preset, In this way, the desired control member response is obtained immediately upon restarting the pump.
  • a first embodiment of the mechanism employed in accomplishing this object of the invention is shown in F105. -7 and includes an L-shaped intermediate member 43 pivoted to the frame at a pivot point 44 and serving to interconnect the adjustment cam 42 and the control pin 32 of the associated ink pump unit 11.
  • a separate cam 42 and intermediate member 43 is provided for each pump unit 11.
  • the rotatable adjustment cam 42 serves as an operating member which transmits motion from its axis against a shoe 46 on one leg of the L of the intermediate member 43.
  • a similar shoe 47 contacts the control pin 32 of the control member 31.
  • the point of contact between the cam 42 and the adjacent shoe 46 comprises a first separable connection acting in one direction and tending to rotate the intermediate member 43 in a clockwise direction as seen in FIGS. 6 and 7.
  • the point of contact between the control pin 32 and its adjacent shoe 47 defines a second separable connection effective to transmit motion from the intermediate member 43 to the control pin 32 in an opposite direction, that is, counterclockwise as seen in FIG. 6.
  • the various links heretofore described are held in normally rigid relationship to one another by first and second resilient means.
  • the first resilient means comprises a tensioned spring 48 for connectively biasing the first separable connection between the cam 42 and the shoe 46.
  • the spring 48 is anchored at one end 50 to the frame 10, and at the other end to a lug 51 on the intermediate member 43.
  • the second resilient means comprises another tensioned spring 52 mounted internally of the frame 10 to connectively bias the second separable connection between the control pin 32 and shoe 47 for positively transmitting motion.
  • the spring 52 is anchored at one end to a pin 53 secured to the frame 10, and at the other to a lug 55 located off center from the pivot point on the control member 31.
  • the spring 52 tends to pull the control member 31 into a position of maximum displacement volume for each revolution of the pump barrel 12. This, in turn, tends to urge the control pin 32 against the shoe 47 and tends to rotate the intermediate member 43 in the previously defined clockwise direction. Without the spring 48, the spring 52 would be effective to lift the shoe 46 free of the cam 42, thus separating the linkage connection at that point.
  • the spring 48 biases the intermediate member 43 in the counterclockwise direction, tending to bias the first separable connection between the cam 42 and the shoe 46 into a solid, motion-transmitting connection.
  • the first resilient means consisting of the spring 48 is predominant, exerting a relatively stronger biasing force than that of the second resilient means. The combined force of the two springs 48 and 52 thus tends to keep the linkage in a solid-motion-transmitting condition from cam 42 to pin 32 so long as the control member 31 is free.
  • the invention provides for a preset adjustment in which the cam 42 may be rotated in either direction, tending to either raise or lower the shoe 46 in respect to the pivot axis of the cam 42. If the control pin 32 is immobilized, the cam 42 may still be moved in a direction tending to transmit motion to the intermediate member 43 in one direction, the clockwise direction as seen in FIGS. 6 and 7.
  • the second separable connection between the pin 32 and shoe 47 simply separates, relieving the linkage from excessive stresses and possible damage.
  • the cam 42 is rotated in a direction which would ordinarily allow the intermediate member 43 to move in the opposite, or counterclockwise direction, as seen in FIGS. 6 and 7.
  • immobility of the control pin 32 prevents the intermediate member 43 from following the cam motion, but the first separable connection between the cam 42 and shoe 46 simply separates, again relieving the system of excessive stresses and possible damage.
  • the superior biasing force of the spring 48 which predominates that of the spring 52, again closes the first separable coupling and makes operating contact between the cam 42 and the shoe 46 as before.
  • the control pin 32 thus is immediately shifted to the preset position which has been fed into the linkage through the cam 42 while the pump unit 11 was immobilized.
  • FIGS. 8, 9 and 10 A second embodiment of the present invention is illustrated in FIGS. 8, 9 and 10.
  • the same pump barrel 12, pistons 26, links 36 and spider 33 are used in conjunction with a modified control member 61 rather than being operated by a pin 32 as in the first embodiment.
  • the control member 61 of the second embodiment is rotated around its vertical axis by an intermediate member comprising two parts, an L-arm 62 and a lever 63, solidly pinned together by a pin 65 (FIG. 10).
  • a disk 66 having an upraised pin 67 which engages the short end of the lever 63.
  • the disk 66 is connected by a shaft 68 to a gear 70 from a worm gear 71 on a cross-shaft 74 which is in turn driven by a set of gears 72, 73 from a main operating shaft 75.
  • a first separable connection 76 is formed at the point of contact of the pin 67 with the short leg of the lever 63. Motion is thereby transferred to the intermediate member composed of the pinned lever 63 and L-arm 62 to the control member 61 through a second separable connection 77 between the longer side of the L-arm 62 and a flat 78 on the lower surface of the control member 61.
  • Resilient means are employed to hold each separable connection 76, 77 in the closed condition when the pump pistons 26 are not immobilized by entrapped ink.
  • a first resilient means consists of the spring 52 which tends to draw the control member 61 into one of its two limit positions.
  • a second resilient means consists of a compression spring 80 operatively connected between the control member 61 and the L-shaped arm 62 of the intermediate member. For this purpose the spring 80 is received within a socket 81 in the control member 61 and is retained on the short arm of the L-arm 62 by a round boss 82.
  • the second resilient means (the spring 80) is stronger than the first resilient means (the spring 52) and is therefore predominant thereto.
  • Zero adjustment in the second embodiment is provided by a threaded adjustable stop 83 retained by a lock nut 84 in a threaded hole in the frame of the machine.
  • the stop 83 has a round tip which bears against an angled surface 85 at one end of the lever 63, thus allowing the limit position of the lever 63 to be selectively adjusted.
  • FIGS. 11, 12 and 13 A third embodiment ofthe present invention is illustrated in FIGS. 11, 12 and 13. Again, the pump barrel l2, pistons 26, links 36, and spider 33 are used. A control member 91 similar to the control member 61 of the second embodiment transfers motion from the operating linkage to the spider 33. A lever 92 is rigidly connected to the control member 91 for transferring motion thereto.
  • the intermediate and adjustment members consist of rotatable plates 93, 95, respectively, journaled on a common axis about a post 96 and retained by a circle clip 97.
  • the lower plate 95 being the adjustment member, has a partial gear section engaging a pinion gear 98 mounted on a vertical shaft 100 through gears 102, 103.
  • the vertical shaft 100 is provided with two additional features. First, a squared end 104 is provided to allow manual adjustment of the mechanism through the pinion 98.
  • a slip clutch is included between the gear 103 and the shaft 100, taking the form of a drive plate 105, a compression plate 106, and a spring 107 which compresses the gear 103 between the plates 105, 106 to frictionally drive the drive plate 105 and thereby drive the vertical shaft 100.
  • the adjustment member rotates about the post 96 within the limits provided by a limit pin 108 which is received within an open segment of the lower plate 95. Ap proximately 75 of rotation is allowed.
  • Motion is transferred from the lower plate 95 to the upper plate 93 by a dog 110 which consists of a round pin pressed into a corresponding hole in the lower plate 95.
  • the upper end of the dog 110 engages a similar cutout section in the upper plate 93, and is normally urged against one face 111 of this plate by a helical spring 112.
  • Spring retainer pins 113, 115 are provided in the plates 95, 93, respectively, to allow the spring 112 to exert a torque tending to urge the upper plate 93 and its operating face 111 against the dog 110, thus forming a first separable connection urged together by a first resilient means.
  • the plate 93 Motion from the intermediate member, the plate 93, is transferred to the control member 91 through a pin 116 in the upper plate 93 which bears on the short edge of the lever 92.
  • the spring 90 provides a second resilient means tending to urge the lever 92 against the pin 116. thereby providing a second separable connection with the spring 90 serving as a second resilient means.
  • the first resilient means (the spring 112) is stronger than and predominant to the second resilient means (the spring 90).
  • a zero adjustment is provided in this embodiment by an ad justable bolt 117 which abuts a fixed pin 118 fixed to the frame of the machine.
  • An extension handle 120 is also provided so that the pump mechanism may be manually adjusted for cleaning and the like.
  • an improved operating linkage comprising an adjustment member. an intermediate member connected for receiving motion in one direction from the adjustment member through a first separable connection and connected for transmitting motion in an opposite direction to the control member through a second separable connection.
  • first resilient means for connectively biasing the first separable connection
  • second resilient means for connectively biasing the second separable connection, whereby the adjustment member may be actuated with the control member in an immovable condition with control member response being effected by the said resilient means upon freeing of the control member.
  • a positive displacement pump having a variable discharge capability comprising, in combination:
  • said pump barrel having a pumping chamber containing a piston mounted for reciprocation therein, said frame having an inlet port and an outlet port communicating with said pumping chamber substantially of pump barrel rotation apart from each other;
  • tiltable swash plate means for varying the reciprocation stroke of the piston
  • control member carrying said swash plate means and being pivoted to the frame for movement between a first limit position corresponding to minimum piston displacement per barrel revolution and a second limit position corresponding to maximum piston displacement per barrel revolution;
  • an adjustment member separably connected to the intermediate member for positively transmitting motion thereto in an opposite direction;
  • first biasing means for resiliently urging said intermediate member into operating contact with said adjustment member
  • second biasing means for resiliently urging said control member into operating contact with said intermediate member.
  • Apparatus as defined in claim 2 including adjustable stop means carried by said frame for selectively adjusting the first limit position of said control member.
  • said first biasing means comprises a spring operatively connected between said intermediate member and said frame
  • said second biasing means comprises a spring operatively connected between said control member and said frame, said first biasing means being predominant over said second biasing means whereby the separable connection between said control and intermediate members is closed when said control member is in a movable condition.
  • said first biasing means comprises a spring operatively connected between said control member and said frame
  • said second biasing means comprises a spring operatively connected between said intermediate member and said control member.
  • said second biasing means being predominant over said first biasing means whereby the separable connection between said control and intermediate members is closed when said control member is in a movable condition.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Inking, Control Or Cleaning Of Printing Machines (AREA)
US773392A 1968-11-05 1968-11-05 Ink injector pump output control mechanism Expired - Lifetime US3534663A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US77339268A 1968-11-05 1968-11-05

Publications (1)

Publication Number Publication Date
US3534663A true US3534663A (en) 1970-10-20

Family

ID=25098119

Family Applications (1)

Application Number Title Priority Date Filing Date
US773392A Expired - Lifetime US3534663A (en) 1968-11-05 1968-11-05 Ink injector pump output control mechanism

Country Status (8)

Country Link
US (1) US3534663A (de)
JP (1) JPS4943602B1 (de)
CH (1) CH505291A (de)
DE (2) DE6942586U (de)
DK (1) DK134245B (de)
FR (1) FR2022619A1 (de)
GB (1) GB1281935A (de)
SE (1) SE361509B (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6152014A (en) * 1989-03-17 2000-11-28 Willimczik; Wolfhart Rotary piston machines

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6152014A (en) * 1989-03-17 2000-11-28 Willimczik; Wolfhart Rotary piston machines

Also Published As

Publication number Publication date
DE1955101A1 (de) 1970-05-27
CH505291A (de) 1971-03-31
DK134245C (de) 1977-02-28
DK134245B (da) 1976-10-04
JPS4943602B1 (de) 1974-11-22
GB1281935A (en) 1972-07-19
DE6942586U (de) 1970-03-26
FR2022619A1 (de) 1970-07-31
SE361509B (de) 1973-11-05

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