Information
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Patent Grant
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6382173
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Patent Number
6,382,173
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Date Filed
Tuesday, May 2, 200024 years ago
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Date Issued
Tuesday, May 7, 200222 years ago
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Inventors
-
Original Assignees
-
Examiners
Agents
-
CPC
-
US Classifications
Field of Search
-
International Classifications
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Abstract
A split-body deactivation valve lifter for use in an internal combustion engine includes a lower body having a substantially cylindrical base and an elongate column extending in an axial direction a predetermined distance above the base. The base is associated with a cam of the internal combustion engine and converts rotary motion of the cam to linear motion of the lower body. A substantially cylindrical upper body defines an axial column bore therein. A portion of the elongate column of the lower body is slidably disposed within the column bore. The upper body is associated with a valve of the internal combustion engine. The upper body is normally coupled to the elongate column of the lower body to thereby transfer vertical movement of the lower body to vertical movement of the upper body. The upper body is selectively decoupled from the lower body such that a lost motion spring prevents movement of one of the bodies from being transferred to movement of the other body.
Description
TECHNICAL FIELD
The present invention relates to valve lifters for use with internal combustion engines, and, more particularly, to a valve lifter which accomplishes cylinder deactivation in internal combustion engines.
BACKGROUND OF THE INVENTION
Automobile emissions are said to be the greatest source of pollution in numerous cities across the country. Automobiles emit hydrocarbons, nitrogen oxides, carbon monoxide and carbon dioxide as a result of the combustion process. The Clean Air Act of 1970 and the 1990 Clean Air Act set national goals of clean and healthy air for all and established responsibilities for industry to reduce emissions from vehicles and other pollution sources. Standards set by the 1990 law limit automobile emissions to 0.25 grams per mile (gpm) non-methane hydrocarbons and 0.4 gpm nitrogen oxides. The standards are predicted to be further reduced by half in the year 2004. It is expected that automobiles will continue to be powered by internal combustion engines for decades to come. As the world population continues to grow, and standards of living continue to rise, there will be an even greater demand for automobiles. This demand is predicted to be especially great in developing countries. The increasing number of automobiles is likely to cause a proportionate increase in pollution. One major challenge facing automobile manufacturers is to reduce undesirable and harmful emissions by improving fuel economy, thereby assuring the increased number of automobiles has a minimal impact on the environment. A method by which automobile manufacturers have attempted to improve fuel economy and reduce undesirable emissions is cylinder deactivation.
Generally, cylinder deactivation is the deactivation of the intake and/or exhaust valves of a cylinder or cylinders during at least a portion of the combustion process. Cylinder deactivation is a proven method by which fuel economy can be improved. In effect, cylinder deactivation reduces the number of engine cylinders within which the combustion process is taking place. With fewer cylinders performing combustion, fuel efficiency is increased and the amount of pollutants emitted from the engine is reduced. For example, in an eight-cylinder engine under certain operating conditions four of the eight cylinders can be deactivated. Thus, combustion would be taking place in only four, rather than in all eight, cylinders. Cylinder deactivation is effective, for example, during part-load conditions when full engine power is not required for smooth and efficient engine operation. Studies have shown that cylinder deactivation can improve fuel economy by as much as fifteen percent.
Conventional methods of achieving cylinder deactivation have been accomplished through modification of various portions of the valve train, and have typically required the addition of components thereto. These conventional methods have typically not fit within the space occupied by conventional drive train components. Thus, the conventional methods of implementing cylinder deactivation have required modification and redesign of engines to provide the additional space within which to house components used to achieve cylinder deactivation.
Therefore, what is needed in the art is a lifter-based device which accomplishes cylinder deactivation.
Furthermore, what is needed in the art is a device which accomplishes cylinder deactivation and is designed to fit within existing space occupied by conventional drive train components.
SUMMARY OF THE INVENTION
The present invention provides a split-body deactivation valve lifter for use with an internal combustion engine.
The invention comprises, in one form thereof, a lower body having a substantially cylindrical base and an elongate column extending in an axial direction a predetermined distance above the base. The base is associated with a cam of the internal combustion engine and converts rotary motion of the cam to vertical motion of the lower body. A substantially cylindrical upper body defines an axial column bore therein. A portion of the elongate column of the lower body is slidably disposed within the column bore. The upper body is associated with a valve of the internal combustion engine. The upper body is normally coupled to the elongate column of the lower body to thereby transfer vertical movement of the lower body to vertical movement of the upper body. The upper body is selectively decoupled from the lower body such that vertical movement of the lower body is not transferred to vertical movement of the upper body.
An advantage of the present invention is that it is received within standard-sized engine bores which accommodate conventional valve lifters.
Another advantage of the present invention is that the deactivation pin assembly includes two pin members, thereby increasing the rigidity, strength, and operating range of the deactivation valve lifter.
BRIEF DESCRIPTION OF THE DRAWINGS
The above-mentioned and other features and advantages of this invention, and the manner of attaining them, will become apparent and be better understood by reference to the following description of one embodiment of the invention in conjunction with the accompanying drawings, wherein:
FIG. 1
is an axial cross-sectional view of one embodiment of the split body deactivation valve lifter of the present invention; and
FIG. 2
is an axial cross-sectional view of a second embodiment of the split body deactivation valve lifter of the present invention.
Corresponding reference characters indicate corresponding parts throughout the several views. The exemplifications set out herein illustrate one preferred embodiment of the invention, in one form, and such exemplifications are not to be construed as limiting the scope of the invention in any manner.
DESCRIPTION OF THE PREFERRED EMBODIMENT
Referring now to the drawings and particularly to
FIG. 1
, there is shown one embodiment of a split body deactivation valve lifter (SBDVL)
10
of the present invention. SBDVL
10
includes lower body
12
, upper body
14
, and lost motion spring
15
.
Lower body
12
includes base portion
16
and elongate column
18
. Lower body
12
is preferably constructed of, for example, hardened or hardenable steel. Lower body
12
is substantially cylindrical and has a diameter of, for example, 0.842 inches to thereby be received within a standard-sized lifter bore. However, it is to be understood that lower body
12
can be configured to have a larger or smaller diameter thereby enabling SBDVL to be used in variously-sized lifter bores in internal combustion engines.
Base portion
16
preferably has a substantially cylindrical side wall
20
and defines roller chamber
22
. Shaft orifices
24
and
26
are diametrically opposed on side wall
20
, each extending through side wall
20
and terminating within roller chamber
22
. Each of shaft orifices
24
and
26
include respective chamfer portions
24
a
and
26
a.
Roller
30
is received within roller chamber
22
of base portion
16
. Roller
30
is substantially cylindrical and defines shaft bore
32
therethrough. Shaft
40
passes through shaft bore
32
, having a first end disposed within shaft orifice
24
and a second end disposed within shaft orifice
26
. Shaft
40
is affixed to lower body
12
by, for example, staking. A set of needle bearings
34
is disposed within shaft bore
32
intermediate shaft
40
and roller
30
. Roller
30
rides on the cam (not shown) of internal combustion engine
42
. Roller
30
is configured to translate rotary motion of the cam to vertical motion of lower body
12
. Elongate column
18
of lower body
12
extends in an axial direction a predetermined distance from base portion
16
. Elongate column
18
is substantially cylindrical and defines a cylindrical pin bore
46
therethrough. Ring clip
52
is disposed proximate to end
48
.
Upper body
14
includes narrowed sleeve portion
62
interconnected by an axially tapered intermediate portion
64
with top portion
66
. Each of sleeve portion
62
, intermediate portion
64
and top portion
66
are substantially cylindrical. Top portion
66
has a predetermined diameter which is somewhat greater than the diameter of narrowed sleeve portion
62
. Intermediate portion
64
tapers in an axial direction from a wider diameter proximate to top portion
66
to a narrower diameter proximate to sleeve portion
62
. Upper body
14
defines an axial column bore
68
therethrough and a radial deactivation chamber
72
therein. A portion of elongate column
18
of lower body
12
is slidingly disposed within column bore
68
such that pin bore
46
of elongate column
18
is disposed in radial and axial alignment with deactivation chamber
72
. Deactivation pins
74
a,
74
b,
and
74
c
are associated with upper body
14
as described in more detail hereinafter. Upper body
14
is constructed of, for example, hardened or hardenable steel.
Column bore
68
is substantially cylindrical and extends in an axial direction concentrically through upper body
14
. A portion of elongate column
18
is slidingly disposed within and extends through column bore
68
such that end
48
of elongate column
18
extends a predetermined distance from within column bore
68
. Ring clip
52
prevents end
48
of elongate column
18
from entering column bore
68
, and thereby limits axial movement of upper body
14
away from lower body
12
.
Deactivation chamber
72
preferably has substantially cylindrical cross-section and extends a predetermined distance in a radial direction through upper body
14
. More particularly, deactivation chamber
72
begins proximate the outside surface of intermediate portion
64
of upper body
14
and extends radially inward, intersecting column bore
68
, and ends a predetermined distance beyond column bore
68
. Control port
78
is defined by intermediate portion
64
and is in fluid communication with deactivation chamber
72
.
Deactivation pins
74
a,
74
b,
and
74
c
are slidingly disposed within deactivation chamber
72
. Compression spring
82
is disposed intermediate inner side wall
84
of deactivation chamber
72
and deactivation pin
74
c.
Compression spring
82
acts to normally bias deactivation pin
74
c
and, in turn, deactivation pins
74
b
and
74
a
in a direction away from inner side wall
84
of deactivation chamber
72
. C-clip
85
is disposed within deactivation chamber
72
, and acts as a stop to prevent further radial biasing of deactivation pins
74
a,
74
b,
74
c
and establishes a default position for the deactivation pins
74
a,
74
b,
74
c.
In the default or normal operating position, spring
82
biases at least a portion of pin
74
c
into pin bore
46
of elongate column
18
, which is in axial and radial alignment with deactivation chamber
72
. Pin
74
b
is preferably dimensioned to have a length substantially equal to the length of pin bore
46
of elongate column
18
. Thus, the biasing by spring
82
of a portion of pin
74
c
into pin bore
46
results in the biasing of a corresponding portion of pin
74
b
out of pin bore
46
. Pin
74
a
is biased against C-clip
85
. Lower body
12
is thereby coupled to upper body
14
, and reciprocal motion of lower body
12
is transferred to upper body
14
by deactivation pins
74
b
and
74
c.
Each of pins
74
a,
74
b
and
74
c
are substantially cylindrical, and are constructed of, for example, hardened or hardenable steel. Compression spring
82
is constructed of, for example, piano wire or any other material appropriate to bias pins
74
a,
75
b
and
74
c.
Control port
78
is in fluid communication with deactivation chamber
72
, and thus provides a fluid passage through upper body
14
and into deactivation chamber
72
. Pressurized fluid, such as, for example, oil is selectively supplied to control port
78
into deactivation chamber
72
in order to overcome the biasing force exerted by compression spring
82
upon deactivation pins
72
a,
72
b,
and
72
c.
The pressurized fluid acts on face
86
of deactivation pin
74
a
and, in turn, deactivation pin
74
b,
to displace in a radial direction deactivation pin
74
c
from within pin bore
46
, thereby disposing deactivation pin
74
b
entirely within pin bore
46
of elongate column
18
. Thus, lower body
12
is decoupled from upper body
14
, and reciprocal motion of lower body
12
is not transferred to upper body
14
. Most preferably, face
86
of pin
74
a
is a substantially flat surface.
Lost motion spring
15
is disposed intermediate lower body
12
and upper body
14
, and has a first end associated with lower body
12
and a second end associated with upper body
14
. Lost motion spring
15
is a compression spring and acts to bias upper body
14
and lower body
12
axially apart from each other. When lower body
12
is not coupled by deactivation pins
74
b
and
74
c
to upper body
14
, reciprocal motion of lower body
12
compresses lost motion spring
15
. The spring rate of lost motion spring
15
is selected to be a predetermined amount less than the spring rate of the valve spring (not shown). Thus, the compression of lost motion spring
15
does not exert upon upper body
14
a force of sufficient magnitude to compress the valve spring and open the valve (not shown). Thus, the reciprocal motion of lower body
12
is absorbed by lost motion spring
15
, and the corresponding engine valve is not opened. Lost motion spring
15
, by exerting an axial force upon lower body
12
ensures roller
30
maintains contact with the cam (not shown) of internal combustion engine
42
.
In use, roller
30
is associated with and rides on a lobe (not shown) of a cam shaft (not shown) of an internal combustion engine
42
in a conventional manner. Shaft
40
extends through shaft bore
32
in roller
30
and is attached within shaft orifices
24
and
26
, such as, for example, by staking, to lower body
12
. As the engine cam rotates, roller
30
follows the profile of an associated cam lobe and shaft
40
translates the rotary motion of the cam lobe to linear, or vertical, motion of lower body
12
. When deactivation pins
74
a,
74
b
and
74
c
are in their default or normal operating position, spring
82
biases each of deactivation pins
74
a,
74
b,
74
c
away from inner side wall
84
of deactivation pin chamber
72
. Spring
82
biases a portion of deactivation pin
74
c
into pin bore
46
of elongate column
18
which, in turn, biases a portion of deactivation pin
74
b
out of pin bore
46
, thereby coupling lower body
12
to upper body
14
for reciprocal vertical movement.
With deactivation pins
74
a,
74
b,
74
c
in their default positions, vertical movement of lower body
12
is transferred to upper body
14
. Thus, SBDVL
10
vertically reciprocates as one body. The use of at least two deactivation pins
74
b
and
74
c
in transferring the vertical motion balances the forces when lower body
12
is coupled to upper body
14
and SBDVL
10
undergoes vertical reciprocation. Thus, torque upon and bending moments or stresses in SBDVL
10
are reduced. Furthermore, the use of at least two deactivation pins results in a substantially rigid, strong, and durable assembly which can be used at higher engine speeds, or at higher engine revolutions per minute, than an assembly having a single pin. Through valve train linkage (not shown) the reciprocal motion of SBDVL
10
is coupled to and actuates a corresponding intake or exhaust valve (not shown) of internal combustion engine
42
.
Deactivation pins
74
b
and
74
c
are moved out of the default position and placed into a deactivated state by the injection of a pressurized fluid, such as, for example oil or hydraulic fluid, through control port
78
. The injection of the pressurized fluid is selectively controlled by, for example, a control valve (not shown), solenoid (not shown) or other suitable flow control device. The pressurized fluid is injected through control port
78
and into deactivation chamber
72
at a pressure of from about 15 psi to about 50 psi, most preferably about 28 psi or greater. The pressurized fluid fills the portion of deactivation chamber
72
disposed between control port
78
and face
86
of deactivation pin
74
a.
The pressure forces deactivation pin
74
a
radially which, in turn, displaces deactivation pin
74
b
toward inner side wall
84
of deactivation chamber
72
. The displacement of deactivation pin
74
b,
in turn, displaces deactivation pin
74
c
toward inner side wall
84
of deactivation chamber
72
and compresses spring
82
. The length of pin members
74
a,
74
b,
and
74
c
are chosen in conjunction with the spring constant of spring
82
such that, when the pressurized fluid is injected into deactivation chamber
72
, deactivation pin
74
b
is displaced entirely into and disposed entirely within pin bore
46
of elongate column
18
. The portion of deactivation pin
74
c
which was disposed within pin bore
46
is displaced therefrom by deactivation pin
74
b.
Thus, lower body
12
is decoupled from upper body
14
, and vertical reciprocation of lower body
12
is not transferred to upper body
14
.
Close tolerances are preferably maintained between deactivation chamber
72
and the diameter of pin members
74
a,
74
b,
74
c
to thereby increase and maintain the pressure of the injected pressurized fluid against pin member
74
a.
However, some of the pressurized fluid will penetrate into and through deactivation chamber
72
to points between and beyond deactivation pins
74
a,
74
b,
74
c.
Vent and drain passage
88
is defined by upper body
14
and is in fluid communication with deactivation chamber
72
, such that any fluid that is disposed between pin member
74
c
and side wall
84
of deactivation chamber
72
will be pushed out by the displacement of pin members
74
a,
74
b,
74
c
toward side wall
84
by fluid under relatively high pressure. Further, a predetermined amount of leak down is designed into split body deactivation lifter
10
. This leak down occurs in upper body
14
, between elongate column
18
and column bore
68
, thereby lubricating the interface therebetween.
In the decoupled configuration, vertical reciprocation of lower body
12
results in elongate column
18
slidingly reciprocating within column bore
68
. Lost motion spring
15
is alternately compressed and expanded due to vertical reciprocation of lower body
12
. As lost motion spring
15
is compressed by the movement of lower body
12
toward upper body
14
, lost motion spring
15
exerts an axially-directed force on upper body
14
. The spring rate of lost motion spring
15
is selected to be a predetermined amount less than the spring rate of the corresponding valve spring (not shown) of internal combustion engine
42
. Thus, compression of lost motion spring
15
requires a force of a lesser magnitude than does compression of the valve spring required to open the valve. As lost motion spring
15
is compressed, the higher spring rate of the valve spring counteracts the force exerted upon upper body
14
by lost motion spring
15
, thereby preventing the vertical movement of upper body
14
and preventing the associated valve from opening. Thus, the motion of lower body
12
is absorbed by lost motion spring
15
.
Lost motion spring
15
expands as roller
30
follows the return of the cam lobe to its lowest lift profile. The expansion of lost motion spring
15
ensures that roller
30
is maintained in contact with the cam lobe, thereby reducing any excessive clearance or lash between the roller and the cam lobe and minimizing any excessive wear and tear as a result of any such excessive lash. Excessive lash can result in undesirable noise, or lifter clatter, and reduces valve lift and lift duration, all of which contribute to poor and inefficient engine performance. Excessive lash also accelerates wear of a lifter by creating a large gap between the roller and cam lobe. As the cam lobe rotates, it impacts the roller with a sudden and large magnitude force as a result of the large gap between the roller and cam lobe. The sudden and large magnitude impact between the two components significantly increases wear and tear of those components, and may cause premature lifter or valve train failure.
A second embodiment of the split body deactivation valve lifter of the present invention is shown in FIG.
2
. SBDVL
210
is a hydraulic deactivation split body valve lifter, and includes lower body
212
, upper body
214
, and lost motion spring
215
.
Lower body
212
includes base portion
216
having a substantially cylindrical side wall
220
and defines roller chamber
222
. Roller
30
and shaft
40
are received within roller chamber
222
and attached to base portion
216
as described above in regard to SBDVL
10
. Roller
30
is configured to translate rotary motion of the cam to vertical motion of lower body
212
. Lower body
212
further defines column bore
268
, lost motion chamber
270
, and deactivation chamber
272
having side wall
284
.
Column bore
268
extends axially from the top surface of base portion
216
, into and through deactivation chamber
272
, intersecting with and terminating in lost motion chamber
270
. Column bore
268
is substantially concentric with lower body
212
. Deactivation chamber
272
extends in a radial direction a predetermined distance through a portion of base
216
. More particularly, deactivation chamber
272
begins proximate the outside surface of base
216
, extends inward intersecting with column bore
268
, and extends radially a predetermined distance beyond column bore
268
terminating at inner side wall
284
. Control port
278
is defined by base
216
and is in fluid communication with deactivation chamber
272
. Deactivation pins
274
a,
274
b,
274
c
are slidingly disposed within deactivation chamber
272
. Compression spring
282
normally biases deactivation pin
274
c
and, in turn, deactivation pins
274
b
and
274
a
in a radial direction away from inner side wall
284
of deactivation chamber
272
.
Upper body
214
includes elongate column
218
, intermediate portion
264
and top portion
266
. Each of elongate column
218
, intermediate portion
264
and top portion
266
are substantially cylindrical. Elongate column
218
extends a predetermined distance in an axial direction from intermediate portion
264
. Elongate column
218
defines a cylindrical pin bore
246
radially therethrough. A portion of elongate column
218
of upper body
214
is slidingly disposed within column bore
268
such that pin bore
246
of elongate column
218
is disposed in radial and axial alignment with deactivation chamber
272
. Upper body
214
further defines a feed port
219
through which fluid, such as, for example, oil, is injected into SBDVL
210
as is known in conventional hydraulic valve lifters. Upper body
214
is constructed of, for example, hardened or hardenable steel.
Deactivation pins
274
a,
274
b,
and
274
c
are slidingly disposed within deactivation chamber
272
. Compression spring
282
is disposed intermediate inner side wall
284
of deactivation chamber
272
and deactivation pin
274
c.
Compression spring
282
acts to normally bias deactivation pin
274
c
and, in turn, deactivation pins
274
b
and
274
a
in a radial direction away from inner side wall
284
. In a default or normal operating position, spring
282
biases at least a portion of pin
274
c
into pin bore
246
of elongate column
218
, which is in axial and radial alignment with deactivation chamber
272
. Deactivation pin
272
b
is dimensioned to have a length substantially equal to the length of pin bore
246
of elongate column
218
. Thus, the biasing by spring
282
of a portion of pin
274
c
into pin bore
246
results in the displacement of a corresponding portion of deactivation pin
274
b
out of pin bore
246
and into deactivation chamber
272
. Lower body
212
is thereby coupled to upper body
214
. Reciprocal motion of lower body
212
is transferred to upper body
214
by deactivation pins
274
b
and
274
c.
Each of pins
274
a,
274
b,
274
c
are substantially cylindrical, and are constructed of, for example, hardened or hardenable steel.
Control port
278
is in fluid communication with deactivation chamber
272
, and thus provides a fluid passageway through lower body
212
and into deactivation chamber
272
. Pressurized fluid, such as, for example, oil is injected through control port
278
and into deactivation chamber
272
in order to overcome the biasing force exerted by compression spring
282
upon deactivation pins
272
a,
272
b,
272
c.
The pressurized fluid acts to displace deactivation pins
272
a,
272
b,
272
c,
substantially as described above in regard to control port
78
of SBDVL
10
, to decouple lower body
212
from upper body
214
. Thus, lower body
212
is decoupled from upper body
214
, and reciprocal motion of lower body
212
is not transferred to upper body
214
. Preferably, face
286
of deactivation pin
274
a
has a substantially flat surface.
Close tolerances are maintained between deactivation chamber
272
and the diameter of pin members
274
a,
274
b,
274
c
to thereby increase the pressure of the injected pressurized fluid against pin member
274
a.
However, some of the pressurized fluid will penetrate into and through deactivation chamber
272
to points between and beyond deactivation pins
274
a,
274
b,
274
c.
Vent and drain passage
288
is defined by lower body
212
and is in fluid communication with deactivation chamber
272
, such that any fluid that is disposed between pin member
274
c
and side wall
284
of deactivation chamber
272
will be pushed out by the displacement of pin members
274
a,
274
b,
274
c
toward side wall
284
by fluid under relatively high pressure. Vent and drain passage
288
opens at one end into the floor or bottom side of deactivation chamber
272
and is oriented such that reciprocation of SBDVL
210
will facilitate and enhance entrance of fluid into and draining of fluid out of vent and drain passage
288
. Further, a predetermined amount of leak down is designed into split body deactivation lifter
210
. This leak down occurs in lower body
212
, between elongate column
218
and column bore
268
. The leak down flows through lost motion chamber
270
and out drain and vent hole
271
.
Lost motion spring
215
is disposed intermediate lower body
212
and
214
and performs the function as described above in regard to SBDVL
10
. Lost motion spring
215
is selected to have a spring constant a predetermined amount less than the spring constant of the corresponding valve spring (not shown) of internal combustion engine
42
. Further, the spring constant of lost motion spring
215
is selected to be of sufficient magnitude to resist any pump down due to hydraulic pressure acting on upper body
214
. Generally, pump up or pump down occurs in a conventional hydraulic lifter when hydraulic pressure within the lifter is not sufficient to overcome the force of the spring of the valve associated with the lifter, but is sufficient to cause internal expansion of the hydraulic element of the lifter relative to the lifter body. Selecting lost motion spring
215
to have a spring constant of sufficient magnitude enables the lost motion spring to resist the pressures within the hydraulic chamber and prevent pump down. Yet, the spring constant of lost motion spring
215
must be small enough to be compressed by the action of the cam lobe upon roller
30
while SBDVL
210
is in the deactivated or decoupled state.
In the embodiments shown, deactivation pins
72
a,
72
b,
72
c,
and
274
a,
274
b,
274
c
pin bores
46
and
246
and deactivation chambers
72
and
272
are preferably each substantially cylindrical in cross section. It is to be understood that in the present invention each of deactivation pins, pin bore and deactivation chamber can be alternately configured, such as, for example, as having an oval, rectangular, square, or other cross section geometry and still achieve the objects of the present invention.
While the present invention has been described in terms of a preferred embodiment, the present invention can be further modified within the spirit and scope of this disclosure. This application is therefore intended to cover any variations, uses, or adaptations of the present invention using the general principles disclosed herein. Further, this application is intended to cover such departures from the present disclosure as come within the known or customary practice in the art to which this invention pertains and which fall within the limits of the appended claims.
Claims
- 1. A split-body deactivation valve lifter, comprising:a lower body including a base and an column extending in an axial direction a predetermined distance from said base, said base configured for being associated with a cam and for converting motion of the cam to motion of said lower body; a upper body defining an axial column bore therein, a portion of said elongate column of said lower body being slidably disposed within said column bore, said upper body configured for being associated with a valve; and coupling means normally coupling said upper body to said elongate column of said lower body to thereby transfer movement of said lower body to movement of said upper body, said coupling means being configured for selectively decoupling said upper body from said elongate column of said lower body such that movement of said lower body is not transferred to movement of said upper body.
- 2. The split-body deactivation valve lifter of claim 1, wherein:said elongate column of said lower body defines a radial pin bore; said upper body defines a radial deactivation chamber therein; and said coupling means comprises at least one deactivation pin movably carried by said upper body, a first portion of said at least one deactivation pin being normally disposed within said radial pin bore of said elongate column, a second portion of said at least one deactivation pin being normally disposed within said radial deactivation chamber to thereby couple said upper body to said elongate column of said lower body.
- 3. The split-body deactivation valve lifter of claim 2, wherein said upper body defines a control port therein, said control port being in fluid communication with said deactivation chamber, said control port being configured for having a pressurized fluid injected therethrough and into said deactivation chamber to displace said at least one deactivation pin to be completely located within said pin bore of said elongate and thereby decouple said upper body from said elongate column of said lower body.
- 4. The split-body deactivation valve lifter of claim 2, wherein said upper body defines a drain passage, said drain passage being in fluid communication with said deactivation chamber.
- 5. The split-body deactivation valve lifter of claim 2, further comprising biasing means biasing said first portion of said at least one deactivation pin into said radial pin bore of said elongate column, thereby normally coupling said upper body to said elongate column of said lower body.
- 6. The split-body deactivation valve lifter of claim 5, wherein said biasing means comprises a compression spring disposed within said deactivation chamber and exerting a radially-directed force upon said at least one deactivation pin.
- 7. The split-body deactivation valve lifter of claim 1, further comprising a lost motion spring disposed intermediate said lower body and said upper body, said lost motion spring having a first end and a second end, said first end being associated with said lower body, said second end being associated with said upper body.
- 8. The split-body deactivation valve lifter of claim 7, wherein said lost motion spring is a coil spring, said coil spring having a first spring constant, said first spring constant being greater than a second spring constant of a valve spring of the associated valve.
- 9. A split-body deactivation valve lifter for use in an internal combustion engine, said split-body deactivation valve lifter comprising:a lower body having a substantially cylindrical wall interconnected with a top, an elongate column integral with said top and extending in an axial direction a predetermined distance from said top, said elongate column defining a pin bore therethrough, said lower body configured for converting rotary motion of a cam of the engine to linear motion of said lower lifter body; a substantially cylindrical upper body defining a column bore and a deactivation chamber, said column bore extending axially through at least a portion of said upper body, said deactivation chamber extending radially outward from said column bore and through at least a portion of said upper body, at least a portion of said elongate column being slidably disposed within said column bore such that said pin bore is normally disposed in axial and radial alignment with said deactivation chamber, said upper body being associated with a valve of is the internal combustion engine; a deactivation pin assembly disposed partially within said column bore and partially within said deactivation chamber, said deactivation pin assembly normally coupling said elongate column to said upper body to thereby transmit vertical movement of said lower body to vertical movement of said upper body when said deactivation pin assembly is in a default position, said deactivation pin assembly configured for being radially displaced from said default position into a decoupled position to thereby decouple said elongate column from said upper body.
- 10. The split-body deactivation valve lifter of claim 9, wherein said deactivation pin assembly comprises a first outside pin member, a middle pin member, and a second outside pin member, said middle pin member being disposed intermediate said first outside pin member and said second outside pin member, said deactivation pin assembly disposed in said default position when said first outside pin member is disposed entirely within said deactivation chamber, said middle pin member has a first portion disposed within said deactivation chamber and a second portion disposed within said pin bore of said elongate column, said second outside pin member has a first portion disposed within said deactivation chamber and a second portion disposed within said pin bore of said elongate column, said middle pin member and said second outside pin member thereby coupling said elongate column to said upper body to transmit movement of said lower body to movement of said upper body when said deactivation pin assembly is in said default position, said deactivation pin assembly configured for being radially displaced from said default position into a decoupled position wherein said middle pin member is disposed entirely within said pin bore of said elongate column and said first and said second outside pin members are disposed entirely outside of said pin bore of said elongate column to thereby decouple said elongate column from said upper body.
- 11. The split-body deactivation valve lifter of claim 10, wherein each of said deactivation chamber, said first outside pin member, said middle pin member, said second outside pin member, and said pin bore are substantially cylindrical.
- 12. The split-body deactivation valve lifter of claim 10, wherein each of said deactivation chamber, said first outside pin member, said middle pin member, said second outside pin member, and said pin bore are substantially rectangular.
- 13. The split-body deactivation valve lifter of claim 10, wherein said deactivation chamber includes an inner end wall, said second outside pin member being disposed proximate said inner end wall;a compression spring disposed between said second outside pin member and said inner end wall, said compression spring biasing said deactivation pin assembly away from said inner end wall and into said default position.
- 14. The split-body deactivation valve lifter of claim 13, further comprising a C-clip disposed at least partially within said deactivation chamber proximate to said first outside pin member, said C-clip and said first outside pin member in abutting engagement when said deactivation pin assembly is in said default position, said compression spring radially biasing said deactivation pin assembly until said first outside pin member contacts said C-clip.
- 15. The split-body deactivation valve lifter of claim 9, wherein said upper body defines a control port, said control port in fluid communication with said deactivation chamber, said control port configured for having a flow of pressurized fluid injected therethrough and into said deactivation chamber, the pressurized fluid radially displacing said deactivation pin assembly from said default position and into said decoupled position.
- 16. The split-body deactivation valve lifter of claim 9, further comprising a lost motion spring disposed intermediate said lower body and said upper body, said lost motion spring having a first end and a second end, said first end associated with said lower body, said second end associated with said upper body.
- 17. The split-body deactivation valve lifter of claim 16, wherein said lost motion spring has a first spring constant, which is less than a second said spring constant of a valve spring of the associated valve of the internal combustion engine.
- 18. The split-body deactivation valve lifter of claim 17, wherein said lost motion spring comprises a coil spring.
- 19. The split-body deactivation valve lifter of claim 9, further comprising a roller disposed within a roller chamber, defined by said lower body.
- 20. A method of deactivating a cylinder of an internal combustion engine, said method comprising the steps of:providing a lower valve lifter body configured for engaging a cam shaft of the engine, said lower valve lifter body configured for converting rotary motion of the cam to linear motion of said lower valve lifter body; supplying an upper valve lifter body, said upper valve lifter body configured for being associated with a valve of the internal combustion engine, said upper valve lifter body configured for actuating through linear motion the associated valve; normally coupling said lower valve lifter body to said upper valve lifter body to thereby transmit vertical motion of said lower valve lifter body to vertical motion of said upper valve lifter body; and selectively decoupling said lower valve lifter body from said upper valve lifter body such that the motion of said lower valve lifter body is not transmitted to said upper valve lifter body.
- 21. The method of claim 20, wherein said lower valve lifter body includes an elongate column, said upper valve lifter body defines a column bore at least partially therethrough, at least a portion of said elongate column being slidably disposed within said column bore, said normally coupling step comprising the step of coupling said elongate column to said upper valve lifter body.
- 22. The method of claim 21, wherein said normally coupling step further comprises coupling within said column bore said elongate column to said upper valve lifter body.
- 23. The method of claim 21, wherein said upper valve lifter body defines a radial deactivation chamber extending in a radial direction from said column bore, said elongate column defining a pin bore therethrough, said coupling step further comprising the step of disposing a deactivation pin assembly partially within said deactivation chamber and partially within said column bore.
- 24. The method of claim 22, wherein said deactivation pin assembly comprises a first outside pin member, a middle pin member, and a second outside pin member, said middle pin member being disposed intermediate said first outside pin member and said second outside pin member, wherein said coupling step further comprises the steps of normally locating said first outside pin member entirely within said deactivation chamber;normally locating a first portion of said middle pin member being within said deactivation chamber and a second portion of said middle pin member within said pin bore; and normally locating a first portion of said second outside pin member within said pin bore and a second portion of said second outside pin member within said deactivation chamber.
- 25. The method of claim 23, wherein said selectively decoupling step comprises the step of communicating into said deactivation chamber a pressurized fluid, said pressurized fluid pushing on said deactivation pin assembly to displace said first portion of said middle pin member from within said deactivation chamber and into said pin bore, thereby displacing said first portion of said second outside pin member from within said pin bore and into said deactivation chamber.
- 26. The method of claim 20, further comprising the step of absorbing the motion of said lower valve lifter body with a lost motion spring when said lower valve lifter body is decoupled from said upper valve lifter body, said lost motion spring being disposed intermediate said lower valve lifter body and said upper valve lifter body.
- 27. The method of claim 25, further comprising the step of selecting said lost motion spring to have a first spring constant, less than a second spring constant of a valve spring of the associated valve of the internal combustion engine.
US Referenced Citations (7)