AN ELEVATOR MACHINERY BRAKE
FIELD
The invention relates to an elevator machinery brake.
BACKGROUND
An elevator may comprise a car, ashaft, hoisting machinery, ropes,
and a counterweight. A separate or an integrated car frame may surround the
car.
The hoisting machinery may be positioned in the shaft. The hoisting
machinery may comprise a drive, an electric motor, a traction sheave, and a
machinery brake. The hoisting machinery may move the car upwards and
downwards in the shaft. The machinery brake may stop the rotation of the
traction sheave and thereby the movement of the elevator car.
The car frame may be connected by the ropes via the traction
sheave to the counterweight. The car frame may further be supported with
gliding means at guide rails extending in the vertical direction in the shaft. The
guide rails may be attached with fastening brackets to the side wall structures
in the shaft. The gliding means keep the car in position in the horizontal plane
when the car moves upwards and downwards in the shaft. The counterweight
may be supported in a corresponding way on guide rails that are attached to
the wall structure of the shaft.
The car may transport people and/or goods between the landings in
the building. The shaft may be formed so that the wall structure is formed of
solid walls or so that the wall structure is formed of an open steel structure.
The machinery brake may be an electromagnetic brake. The
electromagnetic brake may comprise a frame part and an armature part being
movably attached to the frame part Spring means may be arranged to operate
between the frame part and the armature part in order to push the armature
part away from the frame part when the machinery brake is activated. A brake
shoe acting on a brake surface may be attached to the armature part. The
brake shoe is pushed against the brake surface when the machinery brake is
activated. Electromagnet means may further be arranged in the frame part.
The magnetic field of the electromagnet means pulls the armature part against
the force of the spring means towards the frame part. The machinery brake is
deactivated i.e. the brake shoe is drawn away from the brake surface when the
electromagnet is deactivated.

WO 2012/152998 discloses a damping plate in an electromagnetic
machinery brake. A planar, elastically bendable damping plate is positioned
between a frame part and an armature part in an electromagnetic brake. The
damping plate bends when the armature part hits the frame part and produces
thereby a damping force resisting the bending in order to dampen brake noise.
To generate the damping effect by bending the planar damping plate, the
opposing surfaces of the frame and armature, between which the damping
plate is provided, must both be machined to follow a curvature suitable for
bending the damper plate. For large objects like the machinery brake frame
and armature, this requires an extensive amount of precision machining.
EP 2 868 617 discloses a damping arrangement in an
electromagnetic machinery brake. Several channels are machined around a
magnetization coil in a frame part and in an armature part. At least one
dampening element is fixed with fixing means into each channel. The work
springs providing the thrust to an engaged machinery brake armature are
accommodated in the same channels as the guide pins and dampening
arrangements. Therefore, a tightening bolt needs to be provided for each work
spring to enable work spring tension adjustment for equalization of spring
tension.
SUMMARY
An object of the present invention is an improved elevator
machinery brake.
The elevator machinery brake according to the invention is defined
in claim 1.
The elevator machinery brake comprises:
aframe part having a first surface,
an armature part having a first surface facing towards the first
surface of the frame part, the armature part being movably supported through
at least two supporting points on the frame part, the at least two supporting
points limiting a width of a gap between the first surface of the frame part and
the first surface of the armature part,
spring means fitted at least partly into the frame part and acting
between the frame part and the armature part for pushing the armature part in
a first direction away from the frame part in order to activate the machinery
brake,

electromagnet means fitted into the frame part for pulling the
armature part in a second direction opposite to the first direction against the
force of the spring means towards the frame part in order to deactivate the
machinery brake, whereby each of the supporting points comprises
a longitudinal support pin extending between the armature part and
the frame part for supporting the armature part movably on the frame part and
for limiting the width of the gap,
a sliding bearing surrounding the support pin in the armature part, a
flange of the sliding bearing seating against the first surface of the armature
part,
a damper plate surrounding the support pin in the gap and seating
against the flange of the sliding bearing,
a recess surrounding the support pin in the frame part, said recess
extending from the first surface of the frame part inwards into the frame part,
whereby
the armature part is movable in the first and in the second direction
via the sliding bearing on the support pins,
the flange of the sliding bearing and the damper plate act as
damping elements when the electromagnet means pulls the armature part
towards the frame part,
the damper plate is bendable into the recess when the
electromagnet means pulls the armature part towards the frame part.
Themachinery brake according to the invention provides a simple
construction which still meets all the requirements of the European elevator
standard EN81-20.
The machinery brake may realize three different functionalities with
a simple support arrangement between the armature part and the frame part.
The support arrangement provides as a first functionality force transfer and
guidance for the movement of the armature part in relation to the frame part.
The support arrangement provides as a second functionality dampening when
the armature part hits towards the frame part. The support arrangement
provides as a third functionality agap between the armature part and the frame
part.
The production costs of the machinery brake may be reduced due to
a reduced number of parts needed in the support arrangement and due to a
reduced number of machined surfaces needed in the machinery brake.

DRAWINGS
The invention will in the following be described in greater detail by
means of preferred embodiments with reference to the attached drawings, in
which
Figure 1 shows a side view of an elevator,
Figure 2 shows an axonometric view of an elevator machinery
brake,
Figure 3 shows a cross sectional view of the elevator machinery
brake,
Figure 4 shows a cross sectional view of a fastening arrangement in
the elevator machinery brake..
DETAILED DESCRIPTION
Fig. 1 shows a side view of an elevator.
The elevator may comprise acar 10( an elevatorshaft 20, hoisting
machinery30, ropes 42, and a counterweight41. A separate or an integrated
car frame 11 may surround the car 10.
The hoisting machinery30 may be positioned in the shaft 20. The
hoisting machinery may comprise a drive 31, an electric motor 32, a traction
sheave33, and a machinery brake 100. The hoisting machinery30 maymove
the car 10 in a vertical direction Zupwards and downwards in the vertically
extending elevator shaft 20. The machinery brake 100may stop the rotation of
the traction sheave33 and thereby the movement of the elevator car 10.
The car frame 11 may be connected by the ropes 42 via the traction
sheave33to the counterweight41. The car frame 11 may further be supported
with gliding means 27at guide rails 25extending in the vertical direction in the
shaft 20. The gliding means 27may comprise rolls rolling on the guide rails
25or gliding shoes gliding on the guide rails 25when the car 10 is moving
upwards and downwards in the elevator shaft 20. The guide rails25may be
attached with fastening brackets 26 to the side wall structures 21 in the elevator
shaft 20.The gliding means 27keep the car 10 in position in the horizontal
plane when the car 10 moves upwards and downwards in the elevator shaft
20. The counterweight41may be supported in a corresponding way on guide
railsthat are attached to the wall structure 21 of the shaft 20.
The car 10 may transport people and/or goods between the
landings in the building. The elevator shaft 20 may be formed so that the wall

structure 21 is formed of solid walls or so that the wall structure 21 is formed of
an open steel structure.
Figure 2 shows an axonometric view and figure 3 shows a cross
sectional view of the elevator machinery brake.
The elevator machinery brake 100 may comprise a frame part 50
and an armature part 60.
The armature part 60 may be movably supported through four
supporting points P1, P2, P3, P4on the frame part 50. The support
arrangement in the supporting points P1, P2, P3, P4 will be described more in
detail in connection with figure 4.
The frame part 50 may comprise a first surface 51 and the armature
part 60 may comprises a first surface 61. The first surface 51 of the frame part
50 and the first surface 61 of the armature part 60 are facing towards each
other. The first surface 51 of the frame part 50 may be substantially planar.
The first surface 61 of the armature part 60 may be substantially planar. The
armature part 60 is movable in relation to the frame part 50 so that a width W1
of agap G formed between the first surface 51 of the frame part 50 and the first
surface 61 of the armature part 60 may vary. The frame part 50 is stationary.
The frame part 50 may be attached to a stationary frame construction of the
hoisting machinery 30.
The frame part 50 may further comprise a central bore 57 positioned
in a middle portion of the frame part 50. The central bore 57 may extend
through the frame part 50 from the first surface 51 to the second surface 52 of
the frame part 50. The central bore 57 may be formed of three consecutive
bore portions 57A, 57B, 57C. Each of the bore portions 57A, 57B, 57C may
have a circular cross-section. The diameter of the central bore 57 may
decrease stepwise in the direction from the first surface 51 towards the second
surface 52 of the frame part 50.
The first bore portion 57A may extend inwards into the frame part 50
from the first surface 51 of the frame part 50. The third bore portion 57C may
extend into the frame part 50 from the second surface 52 of the frame part 50.
The second bore portion 57B may extend within the frame part 50 between the
first bore portion 57A and the third bore portion 57C. The second surface 52 is
opposite to the first surface 51 of the frame part 50,
The diameter of the first bore portion 57A may be greater than the
diameter of the second bore portion 57B. A first step T1 may thus be formed in

the transition between the first bore portion 57A and the second bore portion
57B. The diameter of the second bore portion 57B may on the other hand be
greater than the diameter of the third bore portion 57C. A second step T2 may
thus formed in the transition between the second bore portion 57B and the
third bore portion 57C.
The armature part 60 may further comprise a central bore 67
positioned in the middle portion of the armature part 60. The central bore 67
extends through the armature part 60 from the first surface 61 to the second
surface 62 of the armature part 60. The central bore 67 in the armature part 60
may be concentric with the central bore 57 in the frame part 50. The central
bore 67 in the armature part 60 may be formed of two consecutive bore
portions 67A, 67B. Each of the bore portions 67A, 67B may have a circular
cross-section. The first bore portion 67A may extend from the second surface
62 of the armature part 60 inwards into the armature part 60. The second bore
portion 67B may extend from the first surface 61 of the armature part 60
inwards into the armature part 60. The diameter of the first bore portion 67A
may be greater compared to the diameter of the second bore portion 67B. A
step is thus formed between the two bore portions 67A, 67B.
The elevator machinery brake 100 may further comprise spring
means 70 arranged between the frame part 50 and the armature part 60.
The spring means 70 may be fitted at least partly in the frame part
50. The spring means 70 may be supported within the central bore 57 with a
guide pin 53 e.g. a pin bolt extending from the second surface 52 of the frame
part 50 through the central bore 57 into the spring means 70. The guide pin 53
may comprise a head 54 and a body 55 with a threaded portion 55A and a pin
portion 55B. The diameter of the threaded portion 55A of the guide pin 53 may
be greater compared to the diameter of the pin portion 55B of the guide pin 53.
A support plate 56e.g. a washer may be provided on the pin portion 55Bof the
guide pin 53. The hole of the support plate 56 may be smaller than the
diameter of the threaded portion 55A of the guide pin 53. The support plate 56
abuts against the step between the pin portion 55B and the threaded portion
55A. A first end of the spring means 70 may be supported on the support plate
56. The spring means 70 may surround the guide pin 53 at least partly. A
second opposite end of the spring means 70 may be supported on the first
surface 61 of the armature part 60. The compression of the spring means 70
may be regulated by the pin bolt 53. The compression of the spring means 70

is increased when the guide pin 53 is rotated in a clockwise direction i.e. the
guide pin 53 moves downwards in the figure and vice a versa.
The central bore 57 in the frame part 50 may receive the guide pin
53, the support plate 56 and the spring means 70. The central bore 67 in the
armature part 60 may receive at least an outer end of the pin portion 55B of
the guide pin 53. An outer end of the pin portion 55B of the guide pin 53 may
thus move in the first direction S1 and in the second direction S2 in the central
bore 67 in the armature part 60 when the armature part 60 moves in the first
direction S1 and in the second direction S2 in relation to the frame part 50. The
guide pin 53 forms thus a guide for the spring means 70 acting between the
frame part 50 and the armature part 60,
The first end of the spring means 70 may thus be seated against the
first step T1 when the armature part 60 is mounted to the frame part 50. The
spring means 70 may be formed of several curved spring plates stacked upon
each other. The outer threading 55A of the guide pin 53 mates with aninner
treading in the third bore portion 57C in the central bore 57 in the frame part
50. A pre-tensioning of the package of spring plates 70 may be adjusted with
the guide pin 53.
The first end of the spring means 70 may be seating against the
support plate 56 and the lower end of the spring means 70 may be seating
against the first surface 61 of the armature part 60. The force of the spring
means 70 is thus directed in a first direction S1 away from the frame part 50.
The spring means 70 is thus pushing the armature part 60 in the first direction
S1 away from the frame part 50.The spring means 70 will thus activate the
machinery brake 100 in a situation in which the armature part 60 is free to
move in the first direction S1.
The frame part 50 may further comprise a ring recess 58 receiving
electromagnet means 80. The ring recess 58 may have the form of a
ringextending from the first surface of the frame part 50 into the frame part 50.
The ring recess 58 may accommodate a coil for magnetizing the
electromagnet means 80.The electromagnet means 80 may move the
armature part 60 in a second direction S2 against the force of the spring
means 70 towards the frame part 50. The electromagnet means 80 will thus
move the armature part 60 against the force of the spring means 70 in the
second direction S2. The machinery brake 100 will be deactivated when the
electromagnet means 80 is activated, The second direction S2 is opposite to

the first direction S1.
The armature part 60 may be supported on the frame part 50 via
four supporting points P1, P2, P3, P4. Each supporting point P1, P2, P3, P4
may comprise a first bore 59 in the frame part 50, a second bore 69 in the
armature part 60 and a support pin 200 extending in the first bore 59 and in the
second bore 69 between the frame part 50 and the armature part 60. The first
bore 59 in the frame part 50 and the second bore 69 in the armature part 60
are concentric. The support pins 200 may extend from the armature part 60 to
the frame part 50.
At least a middle portion of the frame part 50 i.e. the portion within
the coil may be of a ferromagnetic material e.g. of iron forming a core for the
coil. A current flowing in the coil magnetises the core of the frame part 50.
Magnetization of the core of the frame part 50 will pull the armature part 60
towards the frame part 50. The core concentrates the magnetic flux produced
by the current flowing in the coil.
The armature part 60 may be made of a ferromagnetic material e.g.
of iron: The armature part 60 will thus be attracted to the core 50 when a
current flows in the coil in the electromagnet means 80 in the frame part 50.
The armature part 60 may be attached to a brake shoe 5. The brake
shoe 5 may act on a rotating brake surface provided on a rotating part of the
hoisting machinery 30. The brake shoe 5 and the brake surface on the rotating
part of the hoisting machinery 30 may be planar of curved.
A controller 300 may control the machinery brake 100 i.e. the
electromagnet 80 in the machinery brake 100. The controller 300 may control
the current supplied to the coil in the electromagnet 80.
Figure 4 shows a cross sectional view of a fastening arrangement in
the elevator machinery brake. The figure shows an enlargement of one
supporting point.
The armature part 60 may be movably supported on the frame part
50 through four supportingpoints P1, P2, P3, P4.
Each of the supporting points P1, P2, P3, P4 may comprise
asupportingarrangement 59, 69, 200, 230, 240for supporting the armature part
60 to the frame part 50. The supportingarrangement 59, 69, 200, 230, 240 may
allow movement of the armature part 60 in relation to the frame part 50. The
supportingarrangement 59, 69, 200, 230, 240 may further transfer the brake
torque from the armature part 60 to the frame part 50. Brake torque occurs

when the brake shoe 5 comes into contact with the breaking surface of a
rotating part of the hoisting machinery to brake the motion of the hoisting
machinery 30. The armature part 60 may thus be kept in a position parallel to
the frame part 50 during movement of the armature part 60 in relation to the
frame part 50. The armature part 60 may move in the first direction S1 and in
the opposite second direction S2 in relation to the frame part 50.
The supportingarrangement 59, 69, 200, 230, 240 in each of the
supportingpoints P1, P2, P3, P4 may comprise a first bore 59 extending from
the first surface 51 of the frame part 50 into the frame part 50 to a distance
from a second opposite surface 52 of the frame part 50 and a second bore 69
extending through the armature part 60. A longitudinal centre axis of the first
bore 59 and a longitudinal centre axis of the second bore 69coincide when the
armature part 60 is supported on the frame part 50.
The first bore 59 may be formed of two consecutive bore portions
59A, 59B. Each of the two bore portions 59A, 59B may have a circular cross-
section. The first bore portion 59A may extend inwards from the first surface 51
of the frame part 50. The second bore portion 59B may extend from the inner
end of the first portion 59A further inwards into the frame part 50. The diameter
of the first bore portion 59A may be greater than the diameter of the second
bore portion 59B. A third step T3 may be formed in the transition between the
first bore portion 59A and the second bore portion 59B of the first bore 59.
The second bore 69 may be formed of two consecutive bore
portions 69A, 69B. Each of the two bore portions 69A, 69B may have a circular
cross-section. The first bore portion 69A may extendinwards from a second
surface 62 of the armature part 60. The second bore portion 69B may extend
inwards from the first surface 61 of the armature part 60. The diameter of the
first bore portion 69A may be greater than the diameter of the second bore
portion69B. A fourth step T4may be formed in the transition between the first
bore portion 69A and the second bore portion 69B of the second bore 69.
The support arrangement 59, 69, 200, 230, 240 in each supporting
point P1, P2, P3, P4may further comprise a longitudinal support pin 200, a
sliding bearing 230 and a damper plate 240.
Each support pin 200 may be formed of a bolt having a head
210and a longitudinal body220. The body 220may be formed of two
consecutive body portions 221, 222. Each of the two body portions 221, 222
may have a circular cross-section.The diameter of the body portions 221, 222

may be different. The first body portion 221starting from the head 210may
have a greater diameter compared to the second body portion 222of the
support pin 200. A fifth step T5 is thus formed in the transition between the two
body portions 221, 222 of the support pin 200.
The support pin 200 may pass from a second surface 62 of the
armature part 60 through the second bore 69 in the armature part 60 into the
first bore 59 in the frame part 50. The head 210 of the support pin 200 may be
positioned in the first bore portion 69A of the second bore 69 in the armature
part 60 so that the outer end of the head 210 of the support pin 200 will not in
any event protrude from the second surface 62 of the armature part 60. The
head 210 of the support pin 200 may seat against the fourth step T4 in the
second bore 69 in the armature part 60 and the fifth step T5 of the support pin
200 may seat against the third step T3 in the first bore 59 in the frame part 50
when the support pin 200 is tightened. The width W1 of the gap G between the
armature part 60 and the frame part 50 will be limited by the support pin 200
when the support pin 200 is tightened, i.e. the head 210 is seating against the
fourth step T4 in the second bore 69 and the fifth step T5 of the bolt 200 is
seating against the third step T3 in the first bore 59. The support pin 200 will
allow axial movement of the armature part 60 in relation to the frame part 50
while preventing radial movement of the armature part 60 in relation to the
frame part 50 caused by the brake torque.
The second bore portion 59B of the first bore 59 in the frame part 50
may be provided with an inner threading receiving an outer threading in the
second body portion 222 of the support pin 200.
The sliding bearing 230 may surround the first portion 221 of the
body 220 of the support pin 200 in the armature part 60. The sliding bearing
230 may be formed of a cylinder 231 and a flange 232 at an upper end of the
cylinder 231. The cylinder 231 may be positioned in the second portion 69B of
the second bore 69 in the armature part 60 surrounding the first body portion
221 of the support pin 200. The flange 232 of the sliding bearing 230 may seat
against the first surface 61 of the armature part 60 in the gap G between the
armature part 60 and the frame part 50.
The damper plate 240 may be positioned on the flange 232 of the
sliding bearing 230 in the gap G between the armature part 60 and the frame
part 50. The damper plate 240 may be formed of a circular plate having a
centre bore 241 adapted to the diameter of the first body portion 221 of the

support pin 200. A first surface of the damper plate 240 may face towards the
armature part 60 and a second opposite surface of the damper plate 240 may
face towards the frame part 50.An inner portion of the first surface of the
damper plate 240 is seating against the flange 232 of the sliding bearing 230.
An outer portion of the first surface of the damper plate 240 is at a distance
from the first surface 61 of the armature part 60, whereby said distance is
determined by the thickness of the flange 232 of the sliding bearing 230.
The armature part 60 may move in the axial direction with the sliding
bearing 230on the first body portion 221 of the support pin 200 and thereby in
relation to the frame part 50.
The flange 232 in the sliding bearing 230 and the damper plate 240
act as damping elements when the electromagnet means 80pulls the armature
part 60 towards the frame part 50.
The frame part 50 may further comprise a recess 59C formed at the
outer end of the first bore portion 59A of the first bore 59 in the frame part 50.
The recess 59C may be circular. The diameter of the recess 59C is greater
than the diameter of the first bore portion 59A of the first bore 59 in the frame
part 50. The diameter of the recess 59C may further be greater than the
diameter of the flange 232 of the sliding bearing 230 but smaller than the
diameter of the damper plate 240, The third recess 59C forms thus a cavity
into which an inner portion of the damper plate 240 can bend when the
electromagnet means 80 pulls the armature part 60 against the frame part 50.
The damper plate 240 may be made of spring steel. The flange 232 of the
gliding bearing 230 will press the inner portion of the damper plate 240 into the
cavity 59A when the armature part 60 strikes against the frame part 50.
The length of the first body portion 221 of the support pin 200 may
be determined by the sum of the length L1 from the third step T3 to the first
surface 51 of the frame part 50, the length L2 from the fourth step T4 to the
first surface 61 of the armature part 60 and the maximum width VV1 of the gap
G. The length of the first body portion 221 of the support pin 200 will define the
maximum stroke of the spring means 70. The maximum width W1 of the gap G
should be dimensioned so that the brake shoe 5 may in all circumstances be
able to press with a sufficient force against the brake surface in order to stop
the car 10.
The first body portion 221 of the support pin 200 form the gliding
surface along which the sliding bearing 230 may glide in the first direction S1

and in the second direction S2 when the armature part 60 moves in relation to
the frame part 50. The four support pins 200 are parallel, whereby the first
surface 61 of the armature part 60 will remain parallel to the first surface 51 of
the frame part 50 during the movement of the armature part 60.
The machinery brake operates in the following way:
The controller 300 keeps the electromagnet means 80 in an
activated state i.e. keeps the current supply to the electromagnet means 80
switched on when the elevator is operated in a normal state. The armature part
60 is thus pulled towards the frame part 50, whereby the brake shoe 5 is at a
distance from the brake surface. The hoisting machinery 30 may thus operate
normally.
The controller 300 disconnects the current supply to the
electromagnet means 80 i.e. deactivates the electromagnet means 80, when
the elevator car 10 is to be stopped. Deactivation of the electromagnet means
80 is realized by disconnecting the current flowing through the coil in the
electromagnet means 80 so that the magnetic field keeping the armature part
60 pulled towards the frame part 50 is disconnected. The spring means 70 will
thus push the armature part 60 away from the frame part 50, whereby the
brake shoe 5 will be pushed against the brake surface. The rotation of the
traction sheave 33 will thus be stopped, whereby also the car 10 is stopped.
When the machinery brake 100 starts to open and when the
armature part 60 starts to move towards the frame part 50, the force attraction
exerted on the armature part 60 by the electromagnet means 80 starts to
increase. This is due to the fact that the width W1 of the gap G between the
first surface 51 of the frame part 50 and the first surface 61 of the armature
part 60 starts simultaneously to decrease. The increasing force of attraction
leads to an increase in the kinetic energy of the armature part 60, which may
cause the armature part 60 to noisily strike against the frame part 50.
This problem is eliminated with the damper plate 240, the recess
59C and the bushing 230 used in the invention.
The embodiment shown in the figures shows four supportingpoints
P1, P2, P3, P4 between the frame part 50 and the armature part 60. This may
be an advantageous embodiment, but the invention is not limited to any
specific number of supportingpoints P1, P2, P3, P4. The number of
supportingpoints P1, P2, P3, P4 may be chosen freely according to the needs
in each application. The size of the machinery brake may e.g. influence the

required number of supportingpoints P1, P2, P3, P4.
The supportingpoints P1, P2, P3, P4 are in the embodiment shown
in the figures positioned in the corners of a rectangle radially outside the outer
perimeter of the electromagnet means 80. This may be an advantageous
embodiment, but supportingpoints P1, P2, P3, P4 could in addition and/or
instead be positioned in a different pattern and/or in different positions on the
armature part 60.
The figures show an embodiment in which the frame part 50 and the
armature part 60 have a generally rectangular form. This may be an
advantageous embodiment, but the invention is not limited to any specific form
of the frame part 50 and/or the armature part 60. The frame part 50 and/or the
armature part 60 could e.g. have a circular form or an elliptic form or a
polygonal form.
The figures show an embodiment in which one spring means 70 is
positioned in the middle of the frame part 50. This may be an advantageous
embodiment, but the spring means 70 could be formed of several springs
distributed in any pattern on the frame part 50.
The figures show a spring means 70 formed of several spring plates
placed in a stack. This may be an advantageous embodiment, but any type
and any number of spring means 70 may be used in the invention. The spring
means 70 could e.g. be formed of one or more spring plates or of one or more
coil springs. The spring plates may have a circular form The spring plates may
be curved. The spring plates may be made of spring steel
The figures show an embodiment in which the electromagnet means
80 is formed of one electromagnet surrounding the spring means 70. This is an
advantageous embodiment, but the electromagnet means 80 could be formed
of several electromagnets distributed in any pattern within the frame part 50.
The machinery brake 100 may be used in connection with any kind
of brake. The brake surface on which the brake shoe is acting could be curved
or planar. The brake could be e.g. a drum brake or a disc brake.
The support pins 200 may be formed of bolts The bolts may have a
head 210 and a body 220 extending outwards from the head 210. The body
220 of the bolt 200 may be formed of a first body portion 221 extending
outwards from the head 210 and a second body portion 222 having a smaller
diameter. At least the second body portion 222 of the bolt 200 may be
provided with an outer threading.

The use of the invention is not limited to the elevator disclosed in
the figures. The invention can be used in any type of elevator e.g. an elevator
comprising a machine room or lacking a machine room, an elevator comprising
a counterweight or lacking a counterweight The counterweight could be
positioned on either side wall or on both side walls or on the back wall of the
elevator shaft. The drive, the motor, the traction sheave, and the machine
brake could be positioned in a machine room or somewhere in the elevator
shaft. The car guide rails could be positioned on opposite side walls of the
shaft or on a back wall of the shaft in a so called ruck-sack elevator.
It will be obvious to a person skilled in the art that, as the technology
advances, the inventive concept can be implemented in various ways. The
invention and its embodiments are not limited to the examples described
above but may vary within the scope of the claims.

CLAIMS
1. An elevator machinery brakecomprising
aframe part (50) having a first surface (51),
an armature part (60) having a first surface (61)facing towards the
first surface (51) of the frame part (50), the armature part (60) being movably
supported through at least two supporting points (P1, P2, P3, P4)on the frame
part (50), the at least two supporting points (P1, P2, P3, P4) limiting a width
(W1)of a gap (G) between the first surface (51) of the frame part (50) and the
first surface (61) of the armature part (60),
spring means (70) fitted at least partly into the frame part (50) and
acting between the frame part (50) and the armature part (60) for pushing the
armature part (60) in a first direction (S1) away from the frame part (50) in
order to activate the machinery brake,
electromagnet means (80) fitted into the frame part (50) for pulling
the armature part (60) in a second direction (S2) opposite to the first direction
(S1) against the force of the spring means (70) towards the frame part (50) in
order to deactivate the machinery brake, whereby each of the supporting
points (P1, P2, P3, P4) comprises
alongitudinal support pin (200) extendingbetween the armature part
(60) and the frame part (50) for supporting the armature part (60) movably on
the frame part (50) and for limiting the width (W1) of the gap (G),
asliding bearing (230) surrounding the support pin(200) in the
armature part (60), a flange (232) of the sliding bearing (230) seating against
the first surface (61) of the armature part (60),
a damper plate (240) surrounding the supportpin (200) in the gap
(G) and seating against the flange (232) of the sliding bearing (230),
a recess (59C) surrounding thesupport pin (200) in the frame part
(50), said recess (59C) extending from the first surface (51) of the frame part
(50) inwards into the frame part (50), whereby
the armature part (60) is movable in the first and in the second
direction (S1, S2) via the sliding bearing (230) on the support pins (200),
the flange (232) of the sliding bearing (230) and the damper plate
(240) act as damping elements when the electromagnet means (80)pulls the
armature part (60) towards the frame part (50),
the damper plate (240) is bendable into the recess (59C) when the

electromagnet means (80) pulls the armature part (60) towards the frame part
(50).
2. The elevator machinery brake according to claim 1, wherein a
middle portion of the frame part (50) comprises a central bore (57) formed of
consecutive bore portions (57A, 57B, 57C), the diameter of the central bore
(57) decreasing stepwise in the direction from the first surface (51) towards a
second opposite surface (52) of the frame part (50), the first bore portion (57A)
at the first surface (51) of the frame part (50) receiving the spring means (70)
so that a first end of the spring means (70) is supported in the frame part (50)
and a second opposite end of the spring means (70) is supported on the first
surface (61) of the armature part (60).
3. The elevator machinery brake according to claim 2, wherein a
guide pin (53) extends from the second surface (52) of the frame part (50)
through the central bore (57) into the spring means (70), the guide pin (53)
being attached to the frame part (50) and provided with a support plate (56)
supporting the first end of the spring means (70) so that the spring means (70)
becomes pressed between the support plate (56) and the armature part (60).
4. The elevator machinery brake according to any one of claims 1
to3, wherein the frame part (50) comprises a ring recess (58) surrounding the
central bore (57) and extending inwards from the first surface (51) of the frame
part (50), the ring recess (58) receiving a coil of the electromagnet means (80).
5. The elevator machinery brake according to any one of claims 1 to
4, wherein each supporting point (P1, P2, P3, P4) comprises a first bore (59) in
the frame part (50) having two consecutive bore portions (59A, 59B) with a
different diameter, a third step (T3) being formed in the transition between the
two bore portions (59A, 59B).
6. The elevator machinery brake according to claim 5, wherein each
supporting point (P1, P2, P3, P4) comprises a second bore (69) in the
armature part (60) having two consecutive bore portions (69A, 69B) with a
different diameter, a fourth step (T4) being formed in the transition between the
two bore portions (69A, 69B).
7. The elevator machinery brake according to claim 5 and 6,
wherein the support pin (200) comprises a head (210) and a longitudinal body
(220), the body (220) comprising two consecutive body portions (221, 222), a
diameter of a first body portion (221) starting from the head (210) being greater
than a diameter of a second body portion (222), whereby a fifth step (T5) is

formed in the transition between the first body portion (221) and the second
body portion (222) of the support pin (200).
8. The elevator machinery brake according to claim 7, wherein the
head (210) of the support pin (200) seats against the fourth step (T4) in a
second bore (69) and the fifth step (T5) of the support pin (200) seats against
the third step (T3) in a first bore (59) when the armature part (60) is supported
on the frame part (50) with the support pins (200).
9. The elevator machinery brake according to any one of claims 5 to.
8, wherein the recess (59C) is formed around the first bore (59) in the frame
part (50).

10. The elevator machinery brake according to claim 9, wherein a
diameter of the recess (59C) is smaller than a diameter of the damper plate
(240) but greater than a diameter of the flange (232) of the sliding bearing
(230).
11. The elevator machinery brake according to any one of claims 1
to 10, wherein the support pins (200) are positioned radially outside the ring
recess (58).
12. The elevator machinery brake according to any one of claims 1
to 11, wherein the armature part (60) is supported on the frame part (50)
through four supporting points (P1, P2, P3, P4).
13. The elevator machinery brake according to claim 12, wherein
the support pins (200) are positioned in the corners of a rectangle.
14. An elevator comprising a car (10) movable upwards and
downwards in a shaft (20) by a hoisting machinery (30) comprising a motor
(32), a traction sheave (33) and a machinery brake (100) according to any one
of claims 1 to 13.