US3313258A - Needle jogging mechanisms - Google Patents

Needle jogging mechanisms Download PDF

Info

Publication number
US3313258A
US3313258A US363890A US36389064A US3313258A US 3313258 A US3313258 A US 3313258A US 363890 A US363890 A US 363890A US 36389064 A US36389064 A US 36389064A US 3313258 A US3313258 A US 3313258A
Authority
US
United States
Prior art keywords
needle
needle bar
shaft
pivot
crank
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.)
Expired - Lifetime
Application number
US363890A
Other languages
English (en)
Inventor
Wulbrede Ernst
Sewing Gerhard
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.)
Singer Co
Original Assignee
Singer Co
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 Singer Co filed Critical Singer Co
Priority to US363890A priority Critical patent/US3313258A/en
Priority to DE19651485355 priority patent/DE1485355C3/de
Priority to CH599465A priority patent/CH434942A/de
Priority to GB32878/65A priority patent/GB1065565A/en
Application granted granted Critical
Publication of US3313258A publication Critical patent/US3313258A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • D—TEXTILES; PAPER
    • D05—SEWING; EMBROIDERING; TUFTING
    • D05B—SEWING
    • D05B19/00—Programme-controlled sewing machines

Definitions

  • a zigzag-type sewing machine vibratory motion in a direction transverse to the normal direction of the feeding movement of the work is imparted to the needle bar to produce the staggered punctures of the goods by the needle which are necessary in the formation of zigzag stitches. It is advantageous in the formation of such zigzag stitches to minimize the lateral movement of the needle while the needle is projecting through the goods. While the needle is in the goods, lateral movement can adversely affect the appearance of the seam by stretching or shifting the goods, it can by deflecting the needle be detrimental to proper loop seizure and thus thread concatenation, and such lateral movement can result in needle breakage.
  • the vibratory motion is usually derived from a cam embraced by a fork-shaped pitman which transmits the resultant motion of the cam to a needle bar gate which carries the needle bar.
  • a fork-shaped pitman which transmits the resultant motion of the cam to a needle bar gate which carries the needle bar.
  • the fork-shaped pitman is subject to considerable wear and its operation is very noisy.
  • the motions imparted by such cams become exceedingly harsh when the lateral movement of the needle is curtailed While the needle is projecting through the goods.
  • an object of this invention to provide an improved needle jogging mechanism for sewing machines capable of hi h speed operation in which virtually no lateral movement is imparted to the needle while the needle is projecting through the goods to be sewn.
  • Another object of this invention is to provide a needle jogging mechanism for sewing machines capable of high speed operation in which there is greatly decreased wear of the parts and the operation is much quieter than has heretofore been possible.
  • the above objects of this invention are accomplished by providing a shaft journaled in the bracket arm of the sewing machine and having dual eccentric means on the shaft.
  • a pair of pitmans are pivotally connected in spaced relationship to an integrating link and each pitman is pivotally connected to one of the duel eccentric means.
  • the integrating link is pivotally connected to a swinging arm which is in turn connected to the needle bar gate.
  • means are provided for presetting the neutral position of the needle and the magnitude of needle jogging motion.
  • the resultant motion derived from the dual eccentric means is such that virtually no lateral motion is transmitted to the needle bar gate while the needle is projecting through the goods to be sewn.
  • the pitmans cause much less wear than the conventional fork-shaped pitman and cam arrangement.
  • the needle jogging mechanism may be operated at much greater speed than has heretofore being possible.
  • FIG. 1 is a front elevational view, partly in vertical cross section, of a sewing machine incorporating the present invention
  • FIG. 2 is an enlarged vertical cross sectional view of that portion of the sewing machine of FIG. 1 containing the two eccentrics,
  • FIG. 3 is a detail view of the double eccentrics of FIG. 2 after rotation in a counterclockwise direction of approximately degrees beyond the position illustrated in FIG. 2,
  • FIG. 4 is a cross sectional view taken substantially along the line 44 of FIG. 2,
  • FIG. 5 is a cross sectional view taken transversely of the sewing machine bracket arm and substantially along line 5-5 of FIG. 4, and
  • FIG. 6 is a graph comparing needle jogging motion with needle reciprocation.
  • the invention is illustrated as incorporated in a conventional zigzag-type sewing machine having a frame which includes a work supporting bed 10 having a needle aperture 10a with a hollow standard 11 rising from one end.
  • a hollow bracket arm 12 is connected to the top of the standard and extends laterally over the work supporting bed.
  • the bracket arm terminates at its free end in a hollow head 13.
  • a main drive shaft 20 is journaled in the hollow bracket arm and extends between the standard and the head.
  • a handwheel 21 is mounted on the main drive shaft at the standard end of the machine and rotation is imparted to the main drive shaft by means of a motor driven V-belt (not shown) tracking a belt groove 22 formed in the handwhecl.
  • a needle bar 36 carrying a needle 31 is endwise journaled in a needle bar gate 32 in the hollow head of the sewing machine.
  • the needle bar gate is connected to the end of a slide rod 33 which is endwise slidably mounted in bearings 34 in the hollow bracket arm.
  • guide pins 35 set into the sewing head slidably embrace opposite sides of the needle bar gate to constrain the needle bar gate to translatory motion imparted by the slide rod 33.
  • Endwise reciprocation is imparted to the needle bar in a conventional manner by means of a crank 36 which is connected to the main drive shaft at its head end.
  • a link 37 is pivotally connected between the crankpin 38 of the crank and a pivot pin 39.
  • the pivot pin is connected to a bracket 40 which is clamped to the needle bar.
  • the link is slidable on the pivot pin to permit lateral displacement of the needle bar simultaneously with its endwise reciprocation.
  • a feed dog 41 which may be associated with any conventional work feeding mechanism is located in the work supporting bed.
  • the feed dog advances work fabrics across the work supporting bed along a line of feed in a plane indicated at 42 in FIG. 1.
  • jogging motion of the needle laterally of the line of feed is initiated by opposed identical crank means or eccentrics 50, 51 mounted on a driven transverse shaft 52 journaled in the hollow bracket arm of the sewing machine.
  • a worm wheel 53 is also connected to the shaft on which the eccentrics are mounted, and rotation is transmitted to the worn wheel in timed relationship with the endwise reciprocation of the needle by means of a worm 54 mounted on the main drive shaft.
  • the driven transverse shaft on which the eccentrics are mounted rotates once for every two rotations of the main shaft.
  • the eccentrics are embraced by a pair of pitman straps 55, 56.
  • the pitman straps are pivotally connected in spaced relationship to opposite faces of an integrating link 57 by pivot pins 58, 59.
  • Depending fingers 60 on the integrating link serve to maintain the pitman straps in parallel planes on opposed surfaces of the integrating link.
  • the resultant motion of the integrating link as derived from the eccentrics 50, 51 is transmitted to the needle bar gate 32 by means of a connecting means or swinging arm 61 to which the integrating link is pivotally connected by means of a pivot pin 62 equidistant from the pivot pins 58, 59.
  • the swinging arm is pivotally connected by means of a pivot pin 63 to a bracket 64 clamped on the slide rod 33 to which the needle bar gate is connected.
  • the other end of the swinging arm is formed with bifurcate arms 65 which are journaled on a spacer 66.
  • a transverse bore 67 formed diametrically through the spacer constitutes a sliding connection to a pin 68 which is held in the yoke of an adjustable frame 69 mounted to be turned on a horizontal axis. It is the preset angular orientation of the pin 68 about the axis of the frame 69 which determines what component of the total motion of the swinging arm 61 will be converted into the lateral jogging motion imparted to the needle.
  • the distance from the geometric center of either eccentric 50, 51 to the axis of the pivot pin 58 or 59 respectively by which the eccentrics are operatively connected to the integrating link 57 is approximately 2.25 times the eccentricity of the eccentrics.
  • the distance between the axes of the pivot pins 58, 59 along the integrating link is approximately 2.5 times the eccentricity of the eccentrics, and the height of the isosceles triangle formed by the axes of the pivot pins 58, 59 and 62 is 2.8 times the eccentricity.
  • the axes of the shaft 52 for the eccentrics and of the pivot pin 63 by which the swinging arm 61 is operatively connected to the needle bar gate 32 defines a plane which is substantially mutually perpendicular to a median plane defined by the axes of the shaft for the eccentrics and the pivot pin 62 by which the integrating link 57 is connected to the swinging arm.
  • the distance between the axes of the pivot pins 62, 63 along the swinging arm is approximate ly 12 times the eccentricity of the eccentrics.
  • the neutral position of the needle is set by means of telescoped eccentric bushings 80, 81 which shift the pin 68 laterally.
  • a stud 82 protrudes from the outer surface of the frame 69 and is journaled in the eccentric bushing 80.
  • the eccentric bushing 80 is in turn journaled in the eccentric bushing 81 which is journaled in the hollow standard.
  • a handle 83 is connected to the end of the outermost eccentric bushing 81 and by turning the handle the position of the pin 68 may be shifted bodily within the machine frame to preset the neutral position of the needle.
  • Screw pins 84, 85 protruding from the end of the outermost eccentric bushing 81 coacting with bolt stops 86 held in a bracket 87 define the maximum possible neutral position to the right and left of center.
  • a spring 88 cantilevered on the inside of the hollow standard provides friction to maintain the various settings, and a curvilinear portion 89 formed in the spring embraces the uppermost screw pin 84 to indicate center neutral posi- A tion for the needle.
  • Pivotally connected to the end of the inner eccentric bushing is a slide block 90.
  • the slide block slides in a slideway 91 formed in the bracket 87 which is connected to the inside of the hollow standard.
  • the angular orientation of the pin 68 and hence the maximum displacement of the needle is controlled by a handle 100.
  • the handle 100 is secured on the outer end of a shaft 100 (FIG. 2) that is connected at one end through a link 103 to a slideway member 101 which embraces a slide block 102 pivotally connected to an extension of the frame 69.
  • the slideway member is additionally supported by being pivotally connected at its other end to a link 164.
  • the shaft 52 for the eccentrics rotates one-half as fast as the main drive shaft 20 through the worm 54 and the worm wheel 53 as mentioned previously.
  • the shaft 52 for the eccentrics in the position illustrated in FIG. 2 is oriented in a position corresponding to that indicated as 0 degree in FIG. 6, in which position of parts the needle is both in its lowermost position and its leftmost position when set for zigzag operation and as viewed from the front of the machine.
  • the crosshatched portions indicate the periods during which the needle is penetrating the goods.
  • the main drive shaft 20 rotating in the direction shown by the arrow 111 in FIG. 5 rotates the shaft 52 for the eccentrics 50, 51 in the direction shown by the arrow 112 in FIG. 2.
  • the eccentrics 50, 51 impart virtually no lateral motion to the slide rod 33 and hence to the needle which is still projecting through the goods on the work supporting bed.
  • the pitman straps 55, 56 simply follow the eccentrics 50, 51 to pivot the integrating link 57 about the pivot pin 62 which comprises the pivotal connection of the integrating link to the swinging arm 61.
  • the motion imparted by the eccentrics 50, 51 causes the pivot pin 62 to rise as shown in FIG. 3 and the swinging arm 61 to slide up on the pin 68 to shift the slide rod 33 to the right when the pin 68 is set for zigzag operation.
  • the needle is in approximately its midpoint position in FIG. 3 and the shaft for the eccentrics 52 has rotated approximately degrees beyond the position illustrated in FIG. 2.
  • the needle is shifted to its rightmost position and begins to penetrate the goods a second time. Again from approximately 140 degrees to approximately 220 degrees virtually no lateral motion is imparted to the needle while it is projecting through goods on the work supporting bed.
  • the pitman straps 55, 56 again cause the integrating link 57 to simply pivot around the pivot pin 62. After approximately 220 degrees of rotation, the needle is again jogged to the left until the dwell period for the leftmost needle penetration begins after approximately 320 degrees of rotation of the shaft 52 for the eccentrics.
  • the neutral position of the needle is determined by the orientation of the eccentric bushings 80, 81.
  • the handle 83 When the handle 83 is moved upward, the outer eccentric bushing 31 is rotated clockwise.
  • the inner eccentric bushing 80 which is constrained by the slideway 91 slidingly pivots generally in a counterclockwise direction to shift the stud 82 and the pin 68 downward and to the left as viewed in FIG. 1.
  • the leftward movement of the pin 68 shifts the neutral position of the needle to the left.
  • movement of the handle downward moves the pin upward and to the right to shift the neutral position of the needle to the right.
  • the handle controls the angular orientation of the slideway 101 and the pin 68 which determins the magnitude of the lateral displacement of the needle.
  • the slideway 101 is shifted counterclockwise on the links 103, 104 to shift the frame 69 and the pin 68 clockwise.
  • angular movement of the swinging arm 61 about the pivot pin 63 generates a lateral component of motion as the spacer 66 slides up and down on the pin 68.
  • the periods of dwell imposed by the eccentrics 59, 51 and the integrating link 57 are not affected by the angular orientation of the pin 68.
  • a needle jogging mechanism for a sewing machine having a frame, a work support on the frame having an aperture, a needle bar gate, means connected to the needle bar gate and mounted on the frame for permitting lateral oscillation of the needle bar gate, a needle bar, a needle connected to the needle bar, means for mounting the needle bar on the needle bar gate for endwise reciprocation of the needle into and out of the aperture in the Work support, and means for imparting endwise reciprocation to the needle bar
  • said needle jogging mechanism comprising a shaft, means for journaling the shaft on the frame, means for rotating the shaft in timed relation with reciprocation of the needle, two crank means on the shaft oriented around the shaft in spaced angular relationship to each other, two pitmans, one pitman pivotally connected to one of the crank means and the other pitman pivotally connected to the other of the crank means, and integrating link, first and second pivot means in spaced relation to each other on the intergrating link for connecting the pitmans to the integrating link, connecting means for trasmitting lateral
  • crank means are eccentrics and the pitmans have pitman straps which embrace the eccentrics.
  • the needle jogging mechanism of claim 1 which includes slideway means mounted on the frame, means for slidably connecting the connecting means to the slideway means, and means for changing the angular orientation of the slideway means for changing the amplitude of lateral oscillation of the needle bar gate.
  • the needle jogging mechanism of claim 5 in which the distances between the axes of the shaft and each one of the crank means are equal and relative to the eccen' tricity of the crank means defined as the distance between the axes of the shaft and either one of the crank means; the distances between the axes of the first pivot means and its connected crank means and the second pivot means and its connected crank means are approximately 2.25 times the eccentricity, the distance between the first and second pivot means is approximately 2.5 times the eccentricity, and the height of the isosceles triangle formed by the three pivot means is approximately 2.8 times the eccentricity.

Landscapes

  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Sewing Machines And Sewing (AREA)
US363890A 1964-04-30 1964-04-30 Needle jogging mechanisms Expired - Lifetime US3313258A (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US363890A US3313258A (en) 1964-04-30 1964-04-30 Needle jogging mechanisms
DE19651485355 DE1485355C3 (de) 1964-04-30 1965-04-22 Nadelausschwingmechanismus für Zickzack-Nähmaschinen
CH599465A CH434942A (de) 1964-04-30 1965-04-29 Nadelausschwing-Mechanismus
GB32878/65A GB1065565A (en) 1964-04-30 1965-07-31 Needle jogging mechanisms

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US363890A US3313258A (en) 1964-04-30 1964-04-30 Needle jogging mechanisms

Publications (1)

Publication Number Publication Date
US3313258A true US3313258A (en) 1967-04-11

Family

ID=23432149

Family Applications (1)

Application Number Title Priority Date Filing Date
US363890A Expired - Lifetime US3313258A (en) 1964-04-30 1964-04-30 Needle jogging mechanisms

Country Status (3)

Country Link
US (1) US3313258A (de)
CH (1) CH434942A (de)
GB (1) GB1065565A (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3412700A (en) * 1965-01-05 1968-11-26 Rimoldi C Spa Virginio Amplitude adjustment for a zig-zag sewing machine
US3443538A (en) * 1967-06-13 1969-05-13 Singer Co Needle jogging mechanisms for sewing machines
US4829922A (en) * 1987-07-21 1989-05-16 Kochs Adler Aktiengesellschaft Sewing machine with a needle bar jogging frame
US6058862A (en) * 1997-11-27 2000-05-09 Brother Kogyo Kabushiki Kaisha Link-member swinging apparatus
US20020017227A1 (en) * 2000-05-31 2002-02-14 Aisin Seiki Kabushiki Kaisha Over lock sewing machine

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2250696A (en) * 1938-10-14 1941-07-29 Reece Button Hole Machine Co Sewing mechanism
US2310176A (en) * 1941-05-09 1943-02-02 Singer Mfg Co Needle-vibrating mechanism for sewing machines

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2250696A (en) * 1938-10-14 1941-07-29 Reece Button Hole Machine Co Sewing mechanism
US2310176A (en) * 1941-05-09 1943-02-02 Singer Mfg Co Needle-vibrating mechanism for sewing machines

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3412700A (en) * 1965-01-05 1968-11-26 Rimoldi C Spa Virginio Amplitude adjustment for a zig-zag sewing machine
US3443538A (en) * 1967-06-13 1969-05-13 Singer Co Needle jogging mechanisms for sewing machines
US4829922A (en) * 1987-07-21 1989-05-16 Kochs Adler Aktiengesellschaft Sewing machine with a needle bar jogging frame
US6058862A (en) * 1997-11-27 2000-05-09 Brother Kogyo Kabushiki Kaisha Link-member swinging apparatus
US20020017227A1 (en) * 2000-05-31 2002-02-14 Aisin Seiki Kabushiki Kaisha Over lock sewing machine
US6615757B2 (en) * 2000-05-31 2003-09-09 Aisin Seiki Kabushiki Kaisha Over lock sewing machine

Also Published As

Publication number Publication date
GB1065565A (en) 1967-04-19
DE1485355B2 (de) 1976-03-18
CH434942A (de) 1967-04-30
DE1485355A1 (de) 1970-02-19

Similar Documents

Publication Publication Date Title
JP2017184983A (ja) ミシン
US3368507A (en) Feeding mechanism for sewing machines
US4088085A (en) Sewing device for producing form seams
KR20030051314A (ko) 재봉기의 바늘땀 형성 장치
US3313258A (en) Needle jogging mechanisms
US3783810A (en) Looper driving device with periodically variable speed in zig-zag chainstitch sewing machines
US3285210A (en) Looper drive for chain stitch sewing machines
JPS6241035B2 (de)
US3301207A (en) Looper drive mechanism for chainstitch sewing machines
USRE24005E (en) Knaus ctal
US3645221A (en) Needle operation device in high-speed sewing machines
US3426709A (en) Device for automatically varying the stitch length in a zig-zag sewing machine
US3053207A (en) Sewing machine
KR20040038716A (ko) 재봉틀
US3472188A (en) Parallel feeding mechanism for sewing machines
US3835716A (en) Crank-driven reciprocating mechanisms
US3096737A (en) Fabric feeder mechanism for sewing machine
US2310176A (en) Needle-vibrating mechanism for sewing machines
US2324836A (en) Needle-actuating mechanism for zigzag-stitch sewing machines
US3357384A (en) Feeding mechanism for sewing machine
US1331099A (en) Sewing-machine
US3089444A (en) Zig-zag sewing machines
US2579248A (en) Sewing machine
US4073252A (en) Method for effecting the sewing of a pocket stitch
US3540391A (en) Work feeding mechanism