Patent Application
20170356529
The invention relates to a variable force tensioning assembly for use in conjunction with an endless, flexible, power transmission member. More particularly, the invention relates to a variable force tensioning assembly that maintains a constant tension force on an endless, flexible, power transmission member such as a timing belt or a timing chain, encircling a drive sprocket and at least one driven sprocket used for an internal combustion engine of a motor vehicle.
A tensioner for an endless loop, such as a timing belt or a timing chain, is used to control the endless loop as the endless loop travels around a plurality of sprockets or gears. The slack of the endless loop varies as the temperature in the engine increases and as the endless loop wears. When wear occurs, the endless loop elongates and the slack in the endless loop increases. The increase in slack may cause noise, slippage, or, in the case when the endless loop is a chain, tooth jumping between the chain and sprocket teeth. If the increase of the slack in the endless loop is not taken up, by a tensioner for example, in an engine that uses the endless loop to drive a camshaft, the engine may be damaged because the camshaft timing will be misaligned by several degrees due to the slippage or tooth jumping.
In the case when a hydraulic tensioner is used, the performance of the hydraulic tensioner is based on two primary functions of a check valve. First, oil must flow through a check valve and into a high pressure chamber of the tensioner as the piston extends to take up slack in the endless loop. If the flow restriction of the check valve is too great, the piston will not have enough oil volume to support its extended length. Secondly, as the endless loop begins to push the piston back into the tensioner, the oil wants to flow back out of the check valve. At this point, the check valve ball must move back to seal off the oil passage. If the response time is slow, it takes longer to build up the necessary pressure to support the piston and control of the tension in the endless loop becomes an issue.
A variable force tensioning assembly creates and maintains a tension force on an endless loop used to transmit power. The variable force tensioning assembly includes a body having a cylinder. An outer piston is disposed substantially within the cylinder and slidable therewithin. The outer piston includes an outer piston tube and a chamber divider extending through the outer piston tube. The outer piston and the body define a low rate portion. An inner piston is disposed at least partially within the outer piston tube and is slidable therewithin. The inner piston defines a high rate portion and acts with the outer piston against the body to create a variable force to push against the endless loop to maintain a constant tension in the endless loop.
Advantages of the invention will be readily appreciated as the same becomes better understood by reference to the following detailed description when considered in connection with the accompanying drawings, wherein:
The term “loop,” “belt” or “chain,” as used interchangeably herein, is any power transmission member forming an endless loop and constructed of flexible material or of articulated rigid lengths to permit the member to conform to a radius of curvature of a pulley or sprocket drive face and intended, in use, to be driven in an endless path; and, by contact with the pulley or sprocket drive face, to transmit power to or extract power from the pulley or sprocket. The term “pulley” or “sprocket” as used interchangeably herein, is a device rotatable about an axis and having a drive face radially spaced from the axis of rotation for intended power transferring engagement with a belt or chain to drive the belt or chain on an endless path or to extract power from the belt or chain to drive an output load device. The term “guide roll” as used herein is a device rotatable about an axis and having a belt or chain-contacting face radially spaced from the axis of rotation for intended engagement with the belt or chain to aid in directing the belt or chain along an intended path of travel. A guide roll, as distinguished from a pulley or sprocket, is not intended to provide driving power to, or extract power from, a belt or chain. The term “tensioning arm” as used herein is a member other than a pulley or sprocket engagable with the belt or chain, and which is adjustable or relatively movable with respect to the belt or chain in a direction which causes an increase or decrease in tensile stress in the belt or chain or a take-up of any undesirable belt or chain slack to maintain a desirable drive traction between the belt or chain and the pulley or sprocket drive face. A tensioning arm, as distinguished from a guide roll, has a non-rotatable face portion for contacting the belt or chain, whereby the belt or chain slides over the face portion of the tensioning arm. The term “hydraulic tensioner” as used herein applies to a force for actuating the tensioning arrangement and is derived from or transmitted via the exertion of force on a fluid.
Referring to
Referring to
The variable force tensioning assembly 10 also includes an outer piston, generally shown at 40. The outer piston 40 is disposed substantially within the cylinder 28 of the body 24 and is slidable therewithin. The outer piston 40 includes an outer piston tube 42 and a chamber divider 44. The chamber divider 44 extends through the outer piston tube 42. In the embodiment shown, the chamber divider 44 extends perpendicularly to the outer piston tube 42 and parallel to the abutment surface 36 of the cylinder 28. In the embodiment shown in the Figures, the outer piston tube 42 has a circular cross section. It should be appreciated by those skilled in the art that the outer piston tube 42 may have a cross sectional shape other than a circle without deviating from the concepts of the invention. The chamber divider 44 includes chamber passage 46. In the examples shown in
The variable force tensioning assembly 10 also includes an inner piston 56 disposed substantially within the outer piston tube 42 and slidable therewithin. The inner piston 56, together with the portion of the outer piston tube 42 between the tension arm facing surface 32 and the chamber divider 44 defines a chamber described as a high rate portion 54. It is the inner piston 56 that acts, in conjunction with the outer piston 40, against the body 24 to create a variable force to push against the endless loop 12 vis-a-vis the tensioning arm 20 to maintain a constant tension in the endless loop 12. The inner piston 56 includes a cap surface 58, which abuts the tensioning arm 20, and an inner cylinder 60 having an open end 62 disposed adjacent the chamber divider 44. In addition to the fluid which is received by the inner piston 56, a high rate spring 64 is disposed within the inner piston 56 between the cap surface 58 and the chamber divider 44. The inner piston 56 is slidable with respect to the outer piston 40. A small air vent 66 allows air to escape the high rate portion 54.
A fluid inlet passage 68 extends between an outer surface 70 of the body 24 and the cylinder 28. The fluid inlet passage 68 is the passageway through which the fluid, typically a hydraulic oil, is delivered to the cylinder 28 as well as into the low rate portion 48 and the high rate portion 54. As is shown best in
The clearance 76 between the open end 62 of the inner cylinder 60 and the chamber divider 44 controls the stroke of the piston as the endless loop 12 provides a force on the variable force tensioning assembly 10 vis-à-vis the tensioning arm 20.
When an input force is received by the endless loop 12 forcing the compression of the variable force tensioning assembly 10, the inner 56 and outer 40 pistons compress or reduce the volume inside the low rate 48 and high rate 54 portions. The fluid in the low rate chamber 48 flows out due to its decreasing volume. The reservoir provides fluid to the low rate chamber 48 using negative pressure upon its return to a larger volume. Generally, the low rate chamber 48 keeps enough fluid therein to generate a reaction force when necessary.
An alternative embodiment to the variable force tensioning assembly 110 is shown in
In the alternative embodiment, the variable force tensioning assembly 110 is not a hydraulic assembly. In the place of hydraulics is a ratchet and retainer. Because this embodiment does not incorporate the use of hydraulics, elements such as the check valve 52, small air vent 66, fluid inlet passage 68, and chamber passage 72 are not required. In place of the hydraulics is a ratchet clip 78 and a plurality of ribs 80 that encircle the outer surface relief 174 of the outer piston tube 142. Each of the plurality of ribs 80 includes a shallow side 82 and a steep side 84. That is, the ratio of displacement of the ratchet clip 78 as is moves along the shape of the shallow side 82 is further in the x-direction relative to displacement in the y-direction than occurs when the clip 78 moves along the steep side 84. The ratchet clip 78 is slidably securable to the outer piston 140 and slidable along the plurality of ribs 80 rendering forces required to move the inner piston 156 into the cylinder 128 greater than the forces required to move the inner piston 156 out of the cylinder 128. The variable force tensioning assembly 110 also includes a retaining ring 86.
In this embodiment, the inner piston 156 includes a solid inner cylinder 160 or inner stem 160. The inner cylinder 160 extends through the high rate spring 164 and is retained in place by the retainer ring 86 which is disposed on an inner side 88 of the chamber divider 144. The high rate spring 164 may be implemented using a plurality of disk-shaped springs that collectively act against the inner piston 156. The disk-shaped springs, sometimes referred to as Belleville washers or spring washers, can be oriented in series by stacking the springs on top of each other in an axially-aligned orientation. Or the disk-shaped springs can be arranged in parallel such that the center line of one disk-shaped spring is offset from another disk-shaped spring. And rather than a single module of disk-shaped springs arranged in parallel or series, multiple modules each comprising a plurality of disk-shaped springs may be used. It should be understood that the number of disk-shaped springs used to implement the high rate spring 164 can be selected based on a desired spring rate for the high rate spring 164. The quantity, orientation, and/or the size of the disk-shaped springs used to implement the high rate spring 164 can be selected to make the overall stiffness of the spring 164 progressive or regressive. The cap surface 158 is fabricated of a solid material and does not include a small air vent similar to the small air vent 66 found in the first embodiment. Because this embodiment does not include hydraulic fluid, there is no reason to vent air out from the system. The retainer ring 86 is press fit over the inner cylinder 160 to secure the inner piston 156 to the outer piston 140.
The cylinder 128 includes a relief 90 that extends along a portion of the cylinder 128. The relief 90 provides first 92 and second 94 stops preventing the ratchet clip 78 from moving therepast. The first stop 92 prevents the outer piston 140 and the inner piston 156 from leaving the body 124 of the variable force tensioning assembly 110.
Referring to
The invention has been described in an illustrative manner. It is to be understood that the terminology, which has been used, is intended to be in the nature of words of description rather than of limitation.
Many modifications and variations of the invention are possible in light of the above teachings. Therefore, within the scope of the appended claims, the invention may be practiced other than as specifically described.
This application claims benefit of U.S. Provisional Application Ser. No. 62/349,267 filed Jun. 13, 2016, the disclosure of which is herein incorporated by reference in its entirety.
| Number | Date | Country | |
|---|---|---|---|
| 62349267 | Jun 2016 | US |
