The present invention relates to a thermostatic valve for a fluid circulation circuit, in
particular a coolant for a heat engine.
Valves provided with a regulating sleeve whereof the movement is controlled by a
thermostatic element typically equip cooling circuits associated with high-displacement heat
5 engines, in particular those used in trucks and certain motor vehicles, which require higher
coolant flow rates for operation than those encountered for heat engines with lower
displacement, for which the thermostatic valves used have gates.
In fact, using a sleeve generally makes it possible to have a so-called balanced
siiuite; i.=,, a s.-,u:fer for wp,ici; :he difei-ei.ice iii [he presstires aiiing "i, =ifiiei side of ke
I 0 wall of the sleeve is substantially zero in the direction in which the sleeve is moved by the
thermostatic element, that direction in practice corresponding to the axial direction of the
sleeve. Conversely, in a thermostatic valve with a gate, the latter generally extends in a
plane perpendicular to the direction in which the gate is moved by the thermostatic element,
such that the pressure difference prevailing on either side of the gate in that direction
15 reaches high values, in particular when the circulation of fluid is interrupted by the gate. The
energy necessary to unstick such a gate from its seat is then often significant, even more so
when the flow rate of fluid to be regulated is significant and comes in the closing direction of
the gate.
Valves with sleeves integrate a compressed spring that is powerful enough both to
20 return the sleeve to the position it occupied before it was driven by a moving part of the
thermostatic element, and to recall that moving part toward a stationary part of the
thermostatic element, fixedly connected to the valve housing. The opposite ends of this
spring can be arranged respectively bearing against a transverse bridge of the valve housing
and against a force reacting part, movably connected to the sleeve, as proposed in US-A-
25 4,022,377. WO-A-2011/110783, on which the preamble of claim 1 is based, proposes that
the thrust produced by that spring be supported by a rigid yoke, generally made from metal,
that is fixedly connected to the housing, for example by clipping inside the tubular main wall
of the housing: in fine, the housing therefore reacts the opposite forces necessary to fix the
position of the yoke and necessary to fix the position of the thermostatic element,
30 respectively. This housing thus undergoes major mechanical stresses, whereas, in particular
for economic and practical reasons, it is very desirable to make that housing from plastic.
The mechanical strength of the valve is limited as a result.
The aim of the present invention is to propose a thermostatic valve with a sleeve, with
improved mechanical strength, even when the housing of that valve is made from plastic.
35 To that end, the invention relates to a thermostatic valve for a fluid circulation circuit,
as defined in claim 1.
2
One of the ideas at the base of the invention is not to fasten the yoke to the tubular
main wall of the housing, in which the fluid to be regulated by the sleeve circulates, but to
seek to have that yoke react the thrust from the spring and transmit it to the housing closest
to the part of the latter with which the stationary part of the thermostatic element cooperates.
5 Thus, according to the invention, the stationary part of the thermostatic element and the yoke
each cooperate, for the purposes of their respective fastening to the valve housing, with a
same central seating of a bridge that extends across the tubular wall of the housing and that
is fixedly connected to that tubular wall, typically while being integral with that tubular wall in
&% ti.,e even: housing is made from i;iasiic, ii.,e;hai;icai sti.esses Seieia:ed dEi.iiiy
10 use by the thermostatic element and the compressed spring are essentially, or even quasiexclusively,
applied to the central seating of that bridge, having noted that advantageously,
these stresses consist of compression biases of at least part of that central seating, which
can therefore be absorbed without damaging the plastic material making up that central
seating. In particular, even in the event the housing is made from a plastic material, the arms
15 of the bridge, connecting its central seating to the tubular main wall of the housing, only
undergo limited, or even low, forces, which makes it possible to size them to be as small as
possible and thus not to significantly limit the maximum flow rate of the valve according to the
invention.
Additional advantageous features of the valve according to the invention are specified
20 in the dependent claims.
The invention will be better understood upon reading the following description,
provided solely as an example and done in reference to the appended drawings, in which:
- figure 1 is a perspective, longitudinal quarter-cross-sectional view, in which the
edges of the cut parts are not crosshatched for visibility reasons, of a thermostatic valve
25 according to the invention, the sleeve of that valve being shown in a closed position;
- figure 2 is a longitudinal cross-section of the valve of figure 1;
- figure 3 is a longitudinal cross-section of the valve of figure 1, the cutting plane of
figure 3 being identical to that of figure 2, but observed in the opposite direction, figure 3
showing the sleeve in an open position;
30 -figure 4 is an elevation view along arrow IV in figure 3;
-figures 5, 6 and 7 are cross-sections along lines V-V, VI-VI and VII-VII, respectively,
of figure 3; and
-figure 8 is a view similar to figure 2, showing the valve during assembly.
Figures 1 to 8 show a valve 1 suitable for controlling the circulation of a fluid. The
35 valve 1 is for example used in a cooling circuit of a heat engine of a vehicle.
3
The valve 1 comprises a housing 10 in particular made from a plastic material. That
housing 10 includes a tubular main wall 11, which is centered on an axis X-X and which, in
the example embodiment considered in the figures, has a substantially circular base,
centered on the axis X-X. At its opposite axial ends, the wall 11 respectively delimits open
5 orifices 12 and 13, between which the fluid to be regulated by the valve 1 circulates, having
noted that the wall 11 is solid over its entire periphery. In practice, the fluid to be regulated
can circulate from the orifice 12 toward the orifice 13, or in the other direction, depending on
the assembly of the valve 1.
For convenieiice, itlt; iesi of iili Jescripiioii is orieiiiecj i h d axis x,.;i;
10 extends along the vertical and that the orifice 12 is oriented downward, while the orifice 13 is
oriented upward.
The valve 1 also includes a sleeve 20 which, by definition, has a tubular overall
shape, that tubular shape being substantially centered on the axis X-X. In the example
embodiment considered in the figures, the sleeve 20 is positioned outside the housing 10,
15 more specifically on the upper side of the tubular wall 11. The sleeve 20 includes a cylindrical
main body 21, centered on the axis X-X and with a circular base, the wall of which is solid
over its entire periphery. At its lower axial end, i.e., the end turned toward the tubular wall 11
of the housing 10, the body 21 is provided with an outer peripheral rim 22 designed to
cooperate with the upper orifice 13 so as to regulate a flow of fluid between them: more
20 specifically, this rim 22 is designed so as, when the sleeve is in its closed position relative to
the housing 10 as shown in figures 1 and 2, to bear axially, sealably against the perimeter of
the orifice 13, i.e., against the upper end surface of the wall 11, so as to prevent the fluid
from flowing between the rim 22 and the perimeter of the orifice 13. In other words, the
perimeter of the orifice 13 forms an axial bearing seat for the rim 22, that seat being
25 stationary relative to the housing 10. Advantageously, in the embodiment considered in the
figures, the upper end of the tubular wall 11 is outwardly provided with a peripheral sealing
trim 14, against which the outer part of the peripheral rim 22 bears axially, so as to seal the
bearing of that rim against the perimeter of the orifice 13.
When the sleeve is in the open position relative to the housing 10, shown in figure 3,
30 the rim 22 is axially separated from the perimeter of the orifice 13, such that the fluid is free
to flow, in a direction globally radial to the axis X-X, between the rim 22 and the upper end
surface of the wall 11, which amounts to saying that the orifice 13 is then in radial fluid
communication with the outside of the sleeve 20 and the wall 11.
To command the movement of the sleeve 20, in particular between its closed and
35 open positions described above, the valve 1 comprises a thermostatic element 30. In a
known manner, the thermostatic element 30 comprises an upper cup 31, which is
4
substantially centered on the axis X-X and which contains a heat-expandable material, not
shown in the figures, such as a wax. The thermostatic element 30 also comprises a lower
piston 32, which is centered on the axis X-X and which is movable relative to the cup 31 in a
translational movement substantially along the axis X-X. The piston 32 is thus movable under
5 the effect of the expansion of the heat-expandable material contained in the cup 32, the
piston being deployed outside the cup when that material is heated. When the heatexpandable
material cools, the piston 32 retracts inside the cup 31 under the effect of the
decompression thrust from a compressed spring 40.
#qj,"aii(ayeoirsly, i itii txainpie eeibodinie,ii c"iisijered iii ihe flgiires, a iie*;irrg
10 electrical resistance, not shown in the figures, is arranged inside the piston 32, then made in
the form of a heat conducting tube, such that when that resistance is supplied with electricity,
it can heat the heat-expandable material contained in the cup 31. This electrical heating of
the heat-expandable material completes the heating coming from the cup 31 made from a
heat conducting material, that cup itself being heated by the fluid in which the cup 31 is
15 bathed. In practice, depending on the case, these two heat sources participate in similar
proportions or, on the contrary, one is negligible relative to the other, without that being
limiting on the present invention. Furthermore, as one alternative that is not shown, the
aforementioned electrical resistance may be missing, the cup 31 then only being thermally
biased by the fluid in which it is bathed.
20 Returning to the description of the embodiment considered in the figures, it will be
noted that the lower end of the piston 32, i.e., its end emerging from the cup 31, is secured to
a head 33 that cooperates with the housing 10 for the purpose of fastening the piston 32
relative to that housing. More specifically, said head 33, the inside of which is not outlined in
the figures inasmuch as the elements of the inner arrangement are not limiting on the
25 present invention, is received in a complementary housing 16A delimited by the central
seating 16 of a transverse bridge 15 with which the tubular wall 11 of the housing 10 is
inwardly provided.
Thus, as clearly shown in figures 1 to 4, the bridge 15 is fixedly arranged inside the
tubular wall 11 and connects separate portions of the inner face of that wall 11 to each other,
30 while extending protruding from those portions toward the axis X-X. In the example
embodiment considered in the figures, the bridge 15 thus includes three distinct arms 17.1,
17.2 and 17.3, which are distributed substantially regularly around the axis X-X and which
each extend from the inner face of the wall 11, while being integral with that wall, until they
join the central seating 16, which is also integral with those arms. As shown in figures 1 and
35 6, the central seating 16 has a globally tubular shape, which is centered on the axis X-X and
which inwardly delimits the chamber 16A for receiving the head 33 of the piston 32, said
5
chamber 16A being upwardly open, whereas it is downwardly closed by a solid bottom wall
168, as clearly shown in figures 2, 3 and 5.
It will be noted that, in the embodiment considered in the figures, the arms 17.1 to
17.3 are not identical to each other: more specifically, as clearly shown in figures 4 to 6, the
5 arms 17.1 and 17.2 are substantially identical to each other, with the exception of their
angular position around the axis X-X, while the arm 17.3 is provided with a cross-section
strictly larger than that of the arms 17.1 and 17.2. This is related to the fact that here, the arm
17.3 is advantageously used to contain electrical conductors, not shown in the figures, that
tioi.ineci tLiieisid e of itit ii"tisiiiy .ieA i" a base, shwn ;iie figures aii,.jw iih '. :,. . vii ,riz
10 housing 10 is outwardly provided, to connect an outside electrical power source thereto. It
will be understood that these electrical conductors make it possible to power the electrical
resistance contained inside the piston 32 from the aforementioned electricity source, subject
to the electrical connection between the terminals of that resistance and the aforementioned
electrical conductors, via inner arrangement elements of the head 33, not shown in figures,
15 as indicated above. In practice, the aforementioned electrical conductors are embedded in
the plastic material making up the arm 17.3.
For reasons that will appear later, the mechanical connection between the bridge 15
of the housing 10 and the piston 32 of the thermostatic element 30, more specifically
between the central seating 16 of that bridge and the head 33 of that piston, is produced at
20 least by the fixed axial downward bearing of the head 33 against the bottom wall 16B of the
seating 16, that head 33 advantageously being immobilized transversely to the axis X-X
inside the housing 16A by shape adjustment. It is possible for the fixed bearing of the piston
32 against the bridge 15 not to be upwardly blocked by cooperation between that piston and
that bridge. Alternatively, for example by providing a slightly forced mounting or clipping of
25 the head 33 to the inside of the housing 16A, it is possible to retain the piston 32 axially
upward relative to the bridge 15.
In light of the preceding, it will be understood that, in use, the relative movements
between the cup 31 and the piston 32 of the thermostatic element 30 consist of movements
of that cup relative to the housing 10 fixedly connected to the piston 32. Consequently, to
30 control the movement of the sleeve 20 along the axis X-X, that sleeve is kinematically
connected to the cup 31. A first possible approach, not illustrated by the embodiment
considered in the figures, consists of providing a fixed mechanical link between the sleeve 20
and the cup 31.
One alternative, considered here, provides for inserting an overtravel spring 50
35 between them that has a stiffness strictly greater than that of the compression spring 40 and
that is only biased when, once the sleeve 20 has been axially separated from the upper
6
orifice 13 of the housing 10 under the driving action of the cup 31, any additional upward
driving of the sleeve is made impossible, typically due to the upward axial abutment of that
sleeve against a stationary obstacle. Thus, in more detail in the context of the embodiment
considered here, the body 21 of the sleeve 20 is, at its upper end, provided with an inner
5 peripheral rib 23 from which arms 24 belonging to the sleeve 20 extend rigidly toward the
axis X-X. At their free end, these arms 24 are fixedly connected to each other by an annular
crown 25 belonging to the sleeve and substantially coaxial to the body 21. The upper end
turn of the overtravel spring 50 is axially pressed upward against the lower face of that crown
25, wiiiie iiie lower end turn of ilie oveiiravei spring 50 is pressed axiaily ciowr>ward againsi
10 an outer peripheral rim of a jacket 51, which outwardly surrounds the cup 31, while being
fixedly connected to that cup, and around which the crown 25 is mounted freely sliding along
the axis X-X, with a limitation of that sliding in the upward direction by the axial upward
abutment of the crown 25 against a circlips or similar member, fastened on the outer surface
of the sleeve 51. Of course, it is understood that the preceding detailed description, related to
15 the overtravel system including the spring 50 and the jacket 51, is only an illustrative
example, non-limiting with respect to the present invention, inasmuch as other overtravel
assemblies that are functionally similar but structurally different can be considered.
In light of the preceding, it will be understood that, when the cup 31 of the
thermostatic element 30 is translated upward along the axis X-X relative to the piston 32
20 under the effect of the expansion of the heat-expandable material contained by that cup, that
upward translational movement is transmitted to the crown 25 and, subsequently, to the
entire sleeve 20 by the overtravel spring 50, which, when the sleeve 20 is not prevented from
following that translational movement, remains in a substantially unchanged state of
compression: the valve 1 then goes from the configuration shown in figure 2 to the
25 configuration shown in figure 3. In order to drive the sleeve 20 in a reverse translational
movement when the heat-expandable material contracts, the lower end turn 41 of the
compressed spring 40 bears axially downward against the upper face of the crown 25 of the
sleeve 20 such that, under the action of a decompression thrust of the spring 40, the latter is
able to recall the sleeve 20 toward the upper orifice 13 of the housing 10 and the cup 31
30 toward the piston 32 simultaneously. The compression of the spring 40 during the separation
of the sleeve 20 relative to the housing 10, then the release of its decompression thrust to
return that sleeve, are based on the fact that the upper end turn 42 of the spring 40 is axially
upwardly retained relative to the housing 10, by means of a force reacting yoke 60.
This yoke 60 is made from metal or, more generally, from a material capable of
35 withstanding the working stresses produced by the spring 40 without undergoing significant
deformation. This yoke 60 comprises distinct arms 61, which are distributed substantially
7
regularly around the axis X-X and of which there are two in the example embodiment
considered in the figures, while being individually identical to one another. Each arm 61
includes an elongated running part 62 which, when the yoke 60 is in use, i.e., it is assembled
to the other components of the valve 1 in a usage configuration of the valve, as in figures 1 to
5 7, extends lengthwise substantially parallel to the axis X-X, as clearly shown in figures 2 and
3. Advantageously, the running part 62 of each arm 61 has reinforcing folds, aiming in
particular to reinforce the bending strength of that running part.
Toward the top, the running part 62 of each arm 61 extends by an upper end part 63
uf tiia[ a ii,,, .*liich ihi spriiig 40 is -;ixedty io r.-...-: A. irr the ,I Ibirteu. enampie en.,~o~ii.i.,ei,i
10 considered in the figures, this upper end part 63 advantageously has a hook shape, the
recess of which is oriented downward and receives the upper end turn 42 of the spring 40,
that turn 42 bearing axially upwardly against the bottom of the recess of that hook shape.
Toward the bottom, the running part 62 of each arm 61 extends by a lower end part
64 of that arm, the lower end part 64 being suitable for cooperating mechanically with the
15 central seating 16 of the bridge 15 for the purpose of fastening the yoke 60 to the housing
10. To that end, in the embodiment considered in the figures, the two lower end parts 64 are
secured to each other by a bush 65 belonging to the yoke 60 and running all around the axis
X-X, each end part 64 making up a peripheral portion of the bush 65. Advantageously, the
arms 61 and the bush 65 are integral, the yoke 60 being made in the form of a single-piece
20 metal part. As clearly shown in figures 1 to 5, this bush 65 comprises a tubular collar 66,
centered on the axis X-X and relatively non-extended in the direction of that axis, as well as a
bottom wall 67, here provided to be annular, that closes the lower end of the collar 66: the
bush 65 fixedly receives the central seating 16 of the bridge 15, the outer transverse contour
of that seating 16 being substantially adjusted on the inner contour of the collar 66 of the
25 bush 65, while the lower face of the bottom wall 16B of the seating 16 bears axially
downward against the bottom wall 67 of the bush 65. Thus, the yoke 60 is fastened, by its
bush 65, on the central portion 16 of the bridge 15, inasmuch as the upward axial forces
exerted by the compressed spring 40 on the upper end parts 63 of the arms 61 of the yoke
60 are reacted and transmitted by those arms 61 to the bush 65, which, in turn, reacts them
30 and transmits them to the central seating 16, more specifically primarily, or even exclusively,
to the bottom wall 16B of that central seating 16. Optionally, the connection between the
bush 65 of the yoke 60 and the central seating 16 of the bridge 15 can be reinforced so as in
particular to immobilize the latter axially relative to one another in the two opposite directions,
for example by clipping.
35 In practice, each of the two lower end parts 64 of the arms 61 is situated, in a
peripheral direction of the axis X-X, between two of the arms 17.1, 17.2 and 17.3 of the
8
bridge 15, as clearly shown in figure 4, to avoid any interference between them.
Advantageously, the relative angular positioning around the axis X-X, between the central
seating 16 of the bridge 15 and the yoke 60, is fixedly indexed. In the example embodiment
considered in the figures, the bottom wall 16B of the seating 16 has a downward protrusion
5 16C to that end, not centered on the axis X-X, which cooperates by shape matching with a
notch 67A delimited by the bottom wall 67 of the bush 65. Other embodiments can be
considered for these angular indexing elements 16C and 67A.
During use, when the compressed spring 40 is working, the stresses that it exerts on
tili: yoke 60 sre by latter siid :ransii:iiied the ceiili-as;akiiny ;6 [i;; biidgt
10 15, as explained above. Thus, the central seating 16 of the bridge 15 absorbs the respective
fastening stresses of the yoke 60 to the housing 10 and of the piston 32 to that housing. In
other words, the thrust produced by the compressed spring 40 is reacted, via the yoke 60, as
close as possible to the bearing of the piston 32: in particular, the bottom wall 16B undergoes
compression between the downward axial bearing of the piston 32 and the upward axial
15 bearing of the yoke 60, the majority, or even quasi-totality, of the forces related to the
fastening to the housing 10 of the piston 32 and the yoke 60 thus being concentrated on the
axially opposite faces of that bottom wall 16B. In practice, that bottom wall 16B and, more
generally, the central seating 16 of the bridge 15, bears such stresses without damage even
when their values are high, since by nature, the plastic material making up that bottom wall
20 16B has a high level of compressive strength. Furthermore, by thereby concentrating the
fastening forces to the housing 10 on the central seating 16, the rest of the bridge 15, in
particular the arms 17.1, 17.2 and 17.3, are only subjected to limited forces during the work
of the thermostatic element 30 and the work of the compressed spring 40.
Regarding the last aspect mentioned just above, it will be noted that, according to one
25 advantageous embodiment, the spring 40 is assembled to the other components of the valve
1 in a compressed state, i.e., with an axial length strictly smaller than that which the spring
occupies when idle: in this way, the spring 40 continuously produces a decompression thrust
along the axis X-X, which tends both to keep the yoke 60 upwardly bearing against the
central seating 16 of the bridge 15 and to keep the piston 32 downwardly bearing against
30 that same seating 16. It will be understood that it is then not necessary to permanently fixedly
secure the yoke and the piston to the bridge. Furthermore, by providing that the spring 40 is
thus assembled in compression while the valve 1 is in the operating configuration of figures 1
and 2, i.e., when the sleeve 3 closes the perimeter of the upper orifice 13 of the housing 10,
the spring 40 applies its decompression thrust on the sleeve 20 so as to keep it pressed
35 under load against the perimeter of the upper orifice 13, which reinforces the sealing of the
bearing of the sleeve against that perimeter.
9
Furthermore, in the embodiment considered in the figures, the upper axial end of the
body 21 of the sleeve 20 is not closed. On the contrary, fluid may flow axially between the
inside and the outside of the sleeve 20, through the upper end of its body 21: that fluid then
flows, in a direction peripheral to the axis X-X, between the arms 24. Thus, it will be
5 understood that the valve 1 considered in the figures is preferably intended to regulate fluid
between three paths, i.e., between one incoming path and two outgoing paths, or between
two incoming paths and one outgoing path, a first of the three paths being in axial fluid
communication with the inner orifice 12, the second of those three paths being in axial fluid
communicat~onw ith the upper end of the body 2i of the sleeve 20, and the third paih being
10 in radial fluid communication, with interposition of the body 21 of the sleeve 20, with the
upper orifice 13 of the housing 10. In this context, it will be noted that in the embodiment
considered in the figures, the cup 31 of the thermostatic element 30 extends axially upward
past the upper end of the body 21 of the sleeve 20, at least when that sleeve is in its closed
configuration of figures 1 and 2. Likewise, the compressed spring 40 extends axially upward
15 past the upper end of the body 21 of the sleeve 20, at least when that sleeve is in the closing
configuration of figures 1 and 2: in particular, the upper end turn 42 of the spring 40 is
situated at an axial level situated above the upper end of the body 21 of the sleeve 20, at
least when that sleeve is in its closed configuration, as clearly shown in figure 2, such that
the arms 61 extend upward past that end of the body 21 of the sleeve 20. To that end, as
20 clearly shown in figure 7, each of the arms 61 passes, in a direction peripheral to the axis XX,
between two of the arms 24 of the sleeve 20.
Figure 8 illustrates an advantageous optional arrangement of the yoke 60, facilitating
the assembly of the valve 1, i.e., at its lower end part 64, each arm 61 is connected to the
bush 65 deformably between its usage position, shown in figures 1 to 7, and an assembly
25 position, shown in figure 8. To go between these two positions, each arm 61 is moved
relative to the bush 65 by tilting around a geometric axis Z61 extending at the lower end part
64 in a direction substantially orthoradial to the axis X-X, as indicated in figures 2 and 8.
Thus, in its assembly position shown in figure 8, each arm 61 is inclined relative to the axis
X-X, moving upward away from that axis, with the result that the radial distance between the
30 upper end part 63 of the arm and the axis X-X is strictly larger than the radius of the upper
end turn 42 of the spring 40: in that position, the upper end parts 63 of the arms 61 are each
far enough away from the axis X-X to allow the downward axial insertion, without
interference, of at least the spring 40, as well as the overtravel spring 50 and the jacket 51 if
applicable, as well as, potentially, the cup 31 and the piston of the thermostatic element 30.
35 Once the lower end turn 41 of the spring 40 is pressed against the crown 25 of the sleeve 20,
the downward insertion movement is continued, so as to compress the spring 40, until its
10
upper end turn 42 is axially positioned below the axial level of the upper end parts 63 of the
arms 61. While keeping the spring 40 in that compressed state, the arms 61 are then tilted
inward, i.e., toward the axis X-X, around their tilting axis Z61: the upper end parts 63 of the
arms 61 are thus each brought closer to the axis X-X, until those upper end parts are
5 positioned axially overhanging the upper end turn 42, the arms 61 then extending
substantially parallel to the axis X-X. The spring 40 is then released and partially
decompresses, until its upper end turn 42 bears upwardly against the upper end parts 63 of
the arms 61.
In practice, the yoke 60 is manufactured, in particular by stamping, in an ~nitial
10 configuration in which those arms 61 can be either in their assembly position of figure 8, or in
their usage position of figures 1 to 7, or in an intermediate position between the two
aforementioned positions, with the understanding that, during the assembly of the valve 1, an
ad hoc tooling makes it possible, depending on the case, to separate the upper end parts 63
of the arms 61 from the axis X-X or bring them closer thereto, by tilting thereof around
15 respective axes Z61.
As an alternative that is not shown, the functional arrangement of the upper 63 and
lower 64 end parts of each arm 61 may be reversed with respect to the central seating 16 of
the bridge 15 and the turn 42 of the spring 40: in that case, the lower end part of each arm is
free, while being able to cooperate with the central seating 16 for the purpose of fastening
20 the yoke 60 to the housing 10, while the respective upper end parts of the arms are secured
by a corresponding part of the yoke 60, such as the bush 65 for the lower end part 64 in the
embodiment shown in the figures, so as both to cooperate with the turn 42 of the spring 40,
so as to react the thrust produced by the compressed spring 40, and to connect the arm to
that corresponding part of the yoke deformably between a usage position and an assembly
25 position, similar to that described with respect to figures 1 to 7 and that described with
respect to figure 8, respectively.
Lastly, various arrangements and alternatives to the valve 1 described thus far may
be considered. For example:
- the geometry of the housing 10 may be modified relative to that considered in the
30 figures, in particular to adapt to the implantation environment of the valve 1;
- the shape and number of the arms 17.1 to 17.3 and/or the arms 24 andlor the arms
61 are not limited to those shown in figures; and/or
- as an alternative that is not shown, the sleeve 20 can be completely closed at the
upper end of its body 21, the valve 1 then preferably being designed to regulate the flow
35 between only two fluid paths, i.e., one incoming path and one outgoing path; of course, in
that case, unlike the embodiment shown in the figures, it is preferable for none of the
11
components of the valve to pass axially through the wall closing the upper end of the body 21
of the sleeve 20, for example subject to appropriate axial sizing of that body 21.
12

CLAIMS
1.- A thermostatic valve (1) for a fluid circulation circuit, in particular a coolant for a
heat engine, including:
5 - a housing (lo), in particular made from a plastic material, through which a fluid
circulates,
- a sleeve (20) for regulating the circulation of the fluid through the housing, said
sleeve being substantially centered on an axis (X-X) along which the sleeve is movable
reiarlve ro the housing between a closed posiiion, in which ihe sieeve cuts a iiow of fluid, and
10 an open position, in which that flow of fluid is allowed,
- a thermostatic element (30), containing a heat-expandable material and comprising
a stationary part (32), which is fixedly connected to the housing (lo), and a moving part (31),
which is movable along the axis (X-X) relative to the stationary part under the effect of an
expansion of the heat-expandable material and which is kinematically connected to the
15 sleeve (20) so as to command the movement of the sleeve between its closed and open
positions,
- a compression spring (40) to recall the stationary (32) and moving (31) parts of the
thermostatic element (30) toward one another, and
- a yoke (60) for bearing of the spring (40) which, during use, is fixedly connected to
20 the housing (10) and supports the decompression thrust produced by the spring,
characterized in that the housing (10) is inwardly provided with a transverse bridge (15)
including a central seating (16) that cooperates with both the stationary part (32) of the
thermostatic element (30) to connect it fixedly to the housing, and with the yoke (60) to
connect it fixedly to the housing.
25 2.- The valve according to claim 1, characterized in that the central seating (16) of the
bridge (15) is at least partially axially inserted between the yoke (60) and the stationary part
(32) of the thermostatic element (30).
3.- The valve according to one of claims 1 or 2, characterized in that the central
seating (16) of the bridge (15) includes a wall (16B) against the axially opposite faces of
30 which bear, respectively, the yoke (60) under the effect of the thrust produced by the spring
(40) and the stationary part (32) of the thermostatic element (30) under the effect of the
expansion of the heat-expandable material.
4.- The valve according to any one of the preceding claims, characterized in that the
yoke (60) includes arms (61) distributed around the axis (X-X), each arm having two end
35 parts (63, 64), which are opposite one another in the longitudinal direction of the arm and
which, in use, cooperate with the central seating (16) of the bridge (15) in order to be
13
fastened to the housing (10) and with an end (42) of the spring (40) i< order to react the
thrust produced by that spring, respectively.
5.- The valve according to claim 4, characterized in that a first (63) of the two end
parts (63, 64) of each arm (61) is free with respect to the rest of the yoke (lo), while the
5 second end parts (64) of the arms (61) are secured to each other by a corresponding part
(65) of the yoke (GO),
and in that, at its second end part (64), each arm (61) is connected to said corresponding
part (65) of the yoke (GO) deformably between a usage position, in which the first end part
((33) kilt: a,~ii.is, p"s;iioiied o,e,~,aiiyiiiy tiit: (42) 1 ) s piii.iy (40) if; ii le
10 decompression direction of the spring, and an asselnbly position, in which the first end part is
separated, moving away from the axis (X-X), from the place that it occupies when the arm is
in its usage position.
6.- The valve according to claim 5, characterized in that the arms (61) 'and said
corresponding part (65) of the yoke (60) are integral.
15 7.- The valve according to claim 6, characterized in that the yoke (60) is made in the
form of a single-piece metal part.
8.- The valve according to any one of claims 5 to 7, characterized in that each arm.
(61) is movable between its assembly and usage positions by tilting around an axis (261)
substantially orthoradial to the axis (X-X).
20 9.- The valve according to any one of claims 5 to 8, characterized in that, in their use
position, the arms (61) extend substantially parallel to the axis (X-X).
10.- The valve according to any one of claims 5 to 9, characterized in that the first
end part (63) of each arm (61) has a hook shape whereof the recess is suitable for receiving
an end turn (42) of the spring (40), which bears against the bottom of that recess under the
25 effect of the thrust produced by the spring.
11.- The valve according to any one of the preceding claims, characterized in that the
yoke (60) is provided with an angular indexing element (67A) around the axis (X-X), suitable
for cooperating, in particular by shape matching, with an associated element (16C) with
which the central seating (16) of the bridge (15) is provided.