WO1999020919A1 - A motion transforming mechanism - Google Patents

A motion transforming mechanism Download PDF

Info

Publication number
WO1999020919A1
WO1999020919A1 PCT/US1998/022351 US9822351W WO9920919A1 WO 1999020919 A1 WO1999020919 A1 WO 1999020919A1 US 9822351 W US9822351 W US 9822351W WO 9920919 A1 WO9920919 A1 WO 9920919A1
Authority
WO
WIPO (PCT)
Prior art keywords
link
passage
free end
effective length
centre line
Prior art date
Application number
PCT/US1998/022351
Other languages
French (fr)
Inventor
Milan Bajic
Original Assignee
Metal Box South Africa Limited
Handelman, Joseph, H.
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 Metal Box South Africa Limited, Handelman, Joseph, H. filed Critical Metal Box South Africa Limited
Priority to AU12731/99A priority Critical patent/AU1273199A/en
Publication of WO1999020919A1 publication Critical patent/WO1999020919A1/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H21/00—Gearings comprising primarily only links or levers, with or without slides
    • F16H21/10—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane
    • F16H21/44—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for conveying or interconverting oscillating or reciprocating motions

Definitions

  • THIS INVENTION relates to a motion transforming mechanism.
  • the invention relates to a motion transforming mechanism
  • the mechanism may include three links, being the first link, the
  • a first end of the second link may be pivotally connected to an
  • third link being the free end of the third link.
  • the effective length, L, of the first link may be measured
  • effective length, L, of the second link may be measured between its pivotal
  • the first mounting formation proximate the first end of the first
  • link may be in the form of a bore extending through the link, a passage
  • first passage being defined proximate the first end of the
  • first link may be measured as a distance between a centre line of the bore and a centre line of the passage proximate.the opposed end of the first link.
  • a second passage may be defined proximate the opposed end
  • length, L, of the second link may be measured as a distance between a
  • the mechanism may include a drive means to which the first
  • the drive means may, for example, be in the
  • the anchor may
  • cam shaft which is rotatably mounted on a support
  • the element may be mounted, in use, at this
  • the links may then be mounted
  • distance D may be 1 .25L, where L is the effective length of each of the first
  • Figure 1 shows a schematic side view of a motion transforming
  • Figure 2 shows a three dimensional view of the motion transforming
  • reference numeral 1 0 generally designates a
  • the motion transforming mechanism 1 0 comprises a first link
  • the link 1 2 has a mounting formation in the form
  • a passage 1 6 is
  • a second link 1 8 has a first end 1 8. 1 pivotally connected to
  • a further passage 20 is defined at the end
  • length, L has a passage 24 defined at an opposed end 1 8.2.
  • a third link 26, of effective length, 0.5L, is pivotally connected
  • a mounting formation in the form of a bore 32 is defined at an opposed end 26.2 of the link 26.
  • a drive means in the form of a drive shaft 34 is received
  • An anchor in the form of a cam shaft 36 is
  • cam shaft 36 are arranged in a fixed orientation with respect to each
  • the drive shaft 34 and the cam shaft 36 are so arranged that a
  • the drive shaft 34 is connected to a prime mover (not shown)
  • throw of the element 40 can be achieved for imparting a desired linear
  • cam motion can be effected than with conventional cams.
  • the cam motion can be effected than with conventional cams.
  • hygienic aspects are of importance, for example, in the packaging of foodstuffs or beverages.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)

Abstract

A motion transforming mechanism (10) includes a plurality of serially connected links (12, 18, 26), adjacent links being connected in end-to-end relationship to form a chain. A first mounting formation (14) is defined proximate a first, free end of a first link (12) in the chain for mounting the first ink (12) to a drive means which, in use, imparts arcuate, oscillatory motion to said first link (12). A second mounting formation (32) is defined proximate a free end of a last link (26) in the chain for mounting said free end to an anchor so that, in use, the last link (26) is displaceable arcuately about its opposed end, the links (12, 18, 26) being arranged to transform arcuate, oscillatory motion at said free end of the first link (12) into cam motion to an element which, in use, is arranged at a region intermediate the free end of the first link (12) and the free end of the last link (26).

Description

A MOTION TRANSFORMING MECHANISM
THIS INVENTION relates to a motion transforming mechanism.
More particularly, the invention relates to a motion transforming mechanism
for transforming arcuate, oscillatory motion into cam motion.
According to the invention, there is provided a motion
transforming mechanism which includes
a plurality of serially connected links, adjacent links being connected
in end-to-end relationship to form a chain;
a first mounting formation proximate a first, free end of a first link in
the chain for mounting the first link to a drive means which, in use, imparts
arcuate, oscillatory motion to said first link; and
a second mounting formation proximate a free end of a last link in the
chain for mounting said free end to an anchor so that, in use, the last link
is displaceable arcuately about its opposed end, the links being arranged to
transform arcuate, oscillatory motion at said free end of the first link into
cam motion to an element which, in use, is arranged at a region
intermediate the free end of the first link and the free end of the last link.
The mechanism may include three links, being the first link, the
last link and an intermediate, second link, the first link and the second link each being of an effective length, L, and the last, third link being of an
effective length, 0.5L
A first end of the second link may be pivotally connected to an
opposed end of the first link and an opposed end of the second link may be
pivotally connected to a first end of the third link, an opposed end of the
third link being the free end of the third link.
Then, the effective length, L, of the first link may be measured
from its mounting formation to its pivotal connection to the second link, the
effective length, L, of the second link may be measured between its pivotal
connections to the first link and the third link and the effective length, 0.5L,
of the third link may be measured between its pivotal connection to the
second link and the mounting formation of the third link.
The first mounting formation proximate the first end of the first
link may be in the form of a bore extending through the link, a passage
being defined proximate the opposed end of the first link with a
complementary, first passage being defined proximate the first end of the
second link, the passage of the first link and the first passage of the second
link being in alignment with each other with a pivot-axis defining means
being received through said passages. Then, the effective length, L, of the
first link may be measured as a distance between a centre line of the bore and a centre line of the passage proximate.the opposed end of the first link.
A second passage may be defined proximate the opposed end
of the second link with a complementary passage being defined proximate
the first end of the third link, the second passage of the second link and the
passage of the third link being in alignment with each other with a pivot-axis
defining means being received through said passages. Then, the effective
length, L, of the second link may be measured as a distance between a
centre line of its first passage and a centre line of its second passage.
The mounting formation proximate the free end of the third link
may be in the form of a bore extending through the link, the effective
length, 0.5L, of the third link being measured as a distance between a
centre line of the passage of the third link and a centre line of the bore.
The mechanism may include a drive means to which the first
end of the first link is connected, via the first mounting formation, and an
anchor to which the opposed end of the third link is connected, via the
second mounting formation. The drive means may, for example, be in the
form of a drive shaft which is received in the bore of the first link and which
provides arcuate, oscillatory motion to the first link. Then, the anchor may
be in the form of a cam shaft which is rotatably mounted on a support
structure with the cam shaft being received in the bore of the third link. By having the drive shaft and the cam shaft mounted a predetermined distance
apart and extending parallel to each other, cam motion is imparted to the
assembly of links at a junction between the second link and the third link or
along the third link. Then, the element may be mounted, in use, at this
junction, or on the third link, which element moves in a cam-like manner, in
use By appropriate choice of element, the desired cam motion can be
achieved.
To effect the cam-like motion, the links may then be mounted
in use so that the centre line of the bore of the first link is maintained a
fixed distance, D, from the centre line of the bore of the third link. The
distance D may be 1 .25L, where L is the effective length of each of the first
link and the second link.
The invention is now described by way of example with
reference to the accompanying diagrammatic drawings.
In the drawings,
Figure 1 shows a schematic side view of a motion transforming
mechanism, in accordance with the invention, and
Figure 2 shows a three dimensional view of the motion transforming
mechanism. In the drawings, reference numeral 1 0 generally designates a
motion transforming mechanism in accordance with the invention.
The motion transforming mechanism 1 0 comprises a first link
1 2 of effective length, L. The link 1 2 has a mounting formation in the form
of a bore 1 4 defined at a first end 1 2.1 of the link 1 2. A passage 1 6 is
defined at an opposed end 1 2.2 of the link 1 2.
A second link 1 8 has a first end 1 8. 1 pivotally connected to
the end 1 2.2 of the first link 1 2. A further passage 20 is defined at the end
1 8.1 of the link 1 8. A pivot pin 22 is received through the aligned passages
1 6, 20 of the links 1 2, 1 8 respectively, for effecting pivotal connection of
the link 1 8 relative to the link 1 2. The link 1 8, which is also of effective
length, L, has a passage 24 defined at an opposed end 1 8.2.
A third link 26, of effective length, 0.5L, is pivotally connected,
via its first end 26.1 , to the end 1 8.2 of the link 1 8. Thus, a passage 28
is defined through the first end 26.1 of the link 26, the passage 28 being
aligned with the passage 24 at the end 1 8.2 of the link 1 8. A pivot pin 30
is received in the aligned passages 24, 28 to effect pivotal connection of
the link 26 with respect to the link 1 8.
A mounting formation in the form of a bore 32 is defined at an opposed end 26.2 of the link 26.
A drive means in the form of a drive shaft 34 is received
through the bore 1 4 in the link 1 2. The effective length, L, of the link 1 2
is measured between a centre of rotation 34.1 (on a centre line of the bore
1 4) of the drive shaft 34 and a centre of rotation 22.1 (on a centre line of
the passages 1 6,20) of the pivot pin 22. Similarly, the effective length, L,
of the link 1 8 is measured between the centre of rotation 22.1 of the pivot
pin 22 and a centre of rotation 30.1 (on a centre line of the passages
24,28) of the pivot pin 30. An anchor in the form of a cam shaft 36 is
received through the bore 32 in the end 26.2 of the link 26, the cam shaft
36 extending parallel to the drive shaft 34. Once again, the effective
length, 0.5L, of the link 26 is measured between the centre of rotation 30.1
of the pivot pin 30 and a centre of rotation 36.1 (on a centre line of the
bore 32) of the cam shaft 36.
It will be appreciated that, in use, both the drive shaft 34 and
the cam shaft 36 are arranged in a fixed orientation with respect to each
other. The drive shaft 34 and the cam shaft 36 are so arranged that a
distance, D, between the centre of rotation 34.1 of the drive shaft 34 and
the centre of rotation 36.1 of the cam shaft 36 is 1 .25L. In the orientation
of the mechanism 1 0 illustrated in Figure 1 of the drawings, the distance,
D, is measured horizontally. Then, once again, referring to the orientation of the mechanism 1 0 as illustrated in Figure 1 of the drawings, a vertical
distance between the centre of rotation 34.1 of the drive shaft 34 and the
centre of rotation 36. 1 of the cam shaft 36 is L.
In use, a cam-like motion imparting element 40 is connected
to the third link 26. As illustrated, the element 40 is shown connected to
the end 26.1 of the link 26 but it will be appreciated that the element 40
could be connected anywhere along the length of the link 26.
The drive shaft 34 is connected to a prime mover (not shown)
which drives the drive shaft 34 in an arcuate, oscillatory manner to impart
arcuate, oscillatory motion to the first link 1 2 as illustrated by the arrows
38. Due to the connection of the links 1 2, 1 8 and 26 and the positioning
of the drive shaft 34 with respect to the cam shaft 36, arcuate oscillatory
motion imparted to the link 1 2 causes cam-like motion to be imparted to the
element 40 mounted on the link 26.
By appropriate selection of the element 40, accurate dwell and
throw of the element 40 can be achieved for imparting a desired linear
motion to a piece of equipment connected to a free end 40.1 of the element
40, the free end 40. 1 of the element 40 moving in the direction of arrows
42. It is a particular advantage of the invention that the mechanism
1 0 obviates the need for designing and manufacturing complex cam profiles.
It will be appreciated that the design and manufacture of such cams is time
consuming and costly. Further, the applicant believes that a more accurate
cam motion can be effected than with conventional cams. In addition, the
need for a drive shaft which is driven through 360° is obviated, thereby also
obviating the need for cam followers, or the like. Thus, with the provision
of the mechanism 1 0, a more compact piece of equipment results than if
standard cams and followers were to be used. Further, the need for cam
lubricants is obviated which is an important consideration where the
equipment incorporating the mechanism 1 0 is utilized in applications where
hygienic aspects are of importance, for example, in the packaging of foodstuffs or beverages.

Claims

1 . A motion transforming mechanism which includes
a plurality of serially connected links, adjacent links being connected
in end-to-end relationship to form a chain;
a first mounting formation proximate a first, free end of a first link in
the chain for mounting the first link to a drive means which, in use, imparts
arcuate, oscillatory motion to said first link; and
a second mounting formation proximate a free end of a last link in the
chain for mounting said free end to an anchor so that, in use, the last link
is displaceable arcuately about its opposed end, the links being arranged to
transform arcuate, oscillatory motion at said free end of the first link into
cam motion to an element which, in use, is arranged at a region
intermediate the free end of the first link and the free end of the last link.
2. The mechanism as claimed in Claim 1 which includes three
links, being the first link, the last link and an intermediate, second link, the
first link and the second link each being of an effective length, L, and the
last, third link being of an effective length, 0.5L.
3. The mechanism as claimed in Claim 2 in which a first end of
the second link is pivotally connected to an opposed end of the first link and an opposed end of the second link is pivotally connected to a first end of
the third link, an opposed end of the third link being the free end of the third
link.
4. The mechanism as claimed in Claim 3 in which the effective
length, L, of the first link is measured from its mounting formation to its
pivotal connection to the second link, the effective length, L, of the second
link is measured between its pivotal connections to the first link and the
third link and the effective length, 0.5L, of the third link is measured
between its pivotal connection to the second link and the mounting
formation of the third link.
5. The mechanism as claimed in Claim 4 in which the first
mounting formation proximate the first end of the first link is in the form of
a bore extending through the link, a passage being defined proximate the
opposed end of the first link with a complementary, first passage being
defined proximate the first end of the second link, the passage of the first
link and the first passage of the second link being in alignment with each
other with a pivot-axis defining means being received through said
passages.
6. The mechanism as claimed in Claim 5 in which the effective
length, L, of the first link is measured as a distance between a centre line of the bore and a centre line of the passage proximate the opposed end of
the first link.
7. The mechanism as claimed in Claim 5 or Claim 6 in which a
second passage is defined proximate the opposed end of the second link
with a complementary passage being defined proximate the first end of the
third link, the second passage of the second link and the passage of the
third link being in alignment with each other with a pivot-axis defining
means being received through said passages.
8. The mechanism as claimed in Claim 7 in which the effective
length, L, of the second link is measured as a distance between a centre line
of its first passage and a centre line of its second passage.
9. The mechanism as claimed in Claim 7 or Claim 8 in which the
mounting formation proximate the free end of the third link is in the form of
a bore extending through the link, the effective length, 0.5L, of the third link
being measured as a distance between a centre line of the passage of the
third link and a centre line of the bore.
1 0. The mechanism as claimed in Claim 9 in which the links are
mounted in use so that the centre line of the bore of the first link is
maintained a fixed distance, D, from the centre line of the bore of the third link.
1 1 . The mechanism as claimed in Claim 1 0 in which the distance
D is 1 .25L, where L is the effective length of each of the first link and the
second link.
PCT/US1998/022351 1997-10-23 1998-10-22 A motion transforming mechanism WO1999020919A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU12731/99A AU1273199A (en) 1997-10-23 1998-10-22 A motion transforming mechanism

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ZA979505 1997-10-23
ZA97/9505 1997-10-23

Publications (1)

Publication Number Publication Date
WO1999020919A1 true WO1999020919A1 (en) 1999-04-29

Family

ID=25586660

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1998/022351 WO1999020919A1 (en) 1997-10-23 1998-10-22 A motion transforming mechanism

Country Status (2)

Country Link
AU (1) AU1273199A (en)
WO (1) WO1999020919A1 (en)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1135655A (en) * 1912-10-21 1915-04-13 George S Beemer Churn-operating means.
US3488955A (en) * 1968-07-29 1970-01-13 Deere & Co Hydrostatic transmission drive pump swash plate control
US4023423A (en) * 1975-06-19 1977-05-17 Veb Polygraph Leipzig Kombinat Fur Polygraphische Maschinen Und Ausrustungen Variable-stroke and frequency drive
US4848175A (en) * 1987-05-13 1989-07-18 Magnetic-Elektromotoren Gmbh Apparatus for moving pivotable gates and the like

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1135655A (en) * 1912-10-21 1915-04-13 George S Beemer Churn-operating means.
US3488955A (en) * 1968-07-29 1970-01-13 Deere & Co Hydrostatic transmission drive pump swash plate control
US4023423A (en) * 1975-06-19 1977-05-17 Veb Polygraph Leipzig Kombinat Fur Polygraphische Maschinen Und Ausrustungen Variable-stroke and frequency drive
US4848175A (en) * 1987-05-13 1989-07-18 Magnetic-Elektromotoren Gmbh Apparatus for moving pivotable gates and the like

Also Published As

Publication number Publication date
AU1273199A (en) 1999-05-10

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