LATERALLY MOVEABLE COMPRESSOR PISTON ROD LIP SEAL ASSEMBLY

TECHNICAL FIELD

Some example embodiments may generally relate to positive-displacement compressors. For example, certain example embodiments may relate to reciprocating and/or piston compressors.

BACKGROUND

In positive displacement reciprocating gas compressors, gas is compressed in a cylinder between suction up to discharge of the pressure by reciprocating motion on both ends of a double-acting piston. A piston rod (i.e., shaft) is fixed to a double-acting piston, and extends through an opening in a crank-end cylinder head. The piston rod is also connected to a drive train that provides the reciprocating motion. Some pistons also include a piston rod that extends from the other side of the piston through an opening in the head-end head. A pressure packing contains the high-pressure cylinder gas at an annular opening between the crank-end or head-end cylinder head and the piston rod. A wiper packing also prevents crankcase oil from seeping down the piston rod towards the cylinder.

SUMMARY

According to a first embodiment, a piston rod lip seal assembly may include a lip seal including a circumferential lip configured to seal an inner diameter of the lip seal. The piston rod lip seal assembly may further include a heel with clearance over a piston rod, a circumferential outer ring, and a face on a side opposite of the lip seal configured to seal with a cup. The piston rod lip seal assembly may further include a spring. The spring may be disposed between, and in contact with, the circumferential lip and the outer ring.

In a variant, the piston rod lip seal assembly may further include a wave spring.

In a further variant, the piston rod lip seal assembly may also include a pilot.

According to a second embodiment, a piston rod lip seal assembly may include a lip seal including a first circumferential lip configured to seal an inner diameter of the lip seal, and a second circumferential lip configured to seal an outer diameter of the lip seal. The piston rod lip seal assembly may further include a heel and a spring. The spring may be disposed between, in contact with, and secured by the first circumferential lip and the second circumferential lip. The piston rod lip seal assembly may further include a seal carrier disposed around, and in contact with, an outer lip of the lip seal. The seal carrier may further be disposed around, and in contact with, the heel. The seal carrier may be disposed over a piston rod. The seal carrier may further include a barb configured to retain the lip seal axially, and a face on the side opposite from the barb that is configured to seal with the cup.

According to a third embodiment, a piston rod lip seal assembly may include a lip seal including a first circumferential lip configured to seal an inner diameter of the lip seal, and a second circumferential lip configured to seal an outer diameter of the lip seal. The piston rod lip seal assembly may further include a heel including a notch disposed at an inner diameter for an anti-extrusion ring. The anti-extrusion ring may be disposed in the heel. The piston rod lip seal assembly may further include a spring disposed between the first circumferential lip and the second circumferential lip. The piston rod lip seal assembly may further include a seal carrier disposed around, and in sealing contact with, the second circumferential lip. The seal carrier may further be disposed behind, and in contact with, the heel and anti-extrusion ring. The seal carrier may be disposed over the piston rod.

In a variant, the outer ring may include a notch configured to vent gas to a cylinder or transfer oil.

In a variant, the seal carrier may include a notch configured to vent gas to a cylinder.

In a variant, the seal carrier may include a polymer material, a metal material, or a composite material.

In a variant, the spring may be a garter spring, a canted coil spring, a v-spring, an o-ring, and/or any other energizer.

In a variant, the seal carrier may include a pilot for a wave spring to apply an axial preload.

In a variant, the outer ring may include a pilot for a wave spring to apply an axial preload.

In a variant, the seal carrier may further include a barb configured to retain the lip seal axially, and a face on the side opposite from the barb that is configured to seal with the cup.

In a variant, the lip seal may be pegged to a carrier so as to prevent relative rotation.

In a variant, the circumferential lip may include a plurality of points of contact.

In a variant, the piston rod lip seal assembly may be configured to seal oil and/or transfer oil away from the piston rod.

In a variant, the piston rod lip seal assembly may be configured for any diameter piston rod.

In a variant, the piston rod lip seal assembly may be housed in a cylinder in conjunction with a piston seal.

BRIEF DESCRIPTION OF THE DRAWINGS

For a proper understanding of example embodiments, reference should be made to the accompanying drawings, wherein:

FIG. 1A illustrates a perspective view of a first embodiment;

FIG. 1B illustrates another perspective view of the first embodiment;

FIG. 1C illustrates a rear view of the first embodiment;

FIG. 1D illustrates a left-side cross-section view of the first embodiment;

FIG. 1E illustrates a left-side view of the first embodiment;

FIG. 1F illustrates a front view of the first embodiment;

FIG. 2A illustrates a perspective view of the first embodiment with slots;

FIG. 2B illustrates another perspective view of the first embodiment with slots;

FIG. 2C illustrates a rear view of the first embodiment with slots;

FIG. 2D illustrates a left-side cross-section view of the first embodiment with slots;

FIG. 2E illustrates a left-side view of the first embodiment with slots;

FIG. 2F illustrates a front view of the first embodiment with slots;

FIG. 3A illustrates a perspective view of a second embodiment;

FIG. 3B illustrates a rear view of the second embodiment;

FIG. 3C illustrates a left-side cross-section view of the second embodiment;

FIG. 3D illustrates a left-side view of the second embodiment;

FIG. 3E illustrates a front view of the second embodiment;

FIG. 4A illustrates a perspective view of a third embodiment;

FIG. 4B illustrates a rear view of the third embodiment;

FIG. 4C illustrates a left-side cross-section view of the third embodiment;

FIG. 4D illustrates a left-side view of the third embodiment; and

FIG. 4E illustrates a front view of the third embodiment.

DETAILED DESCRIPTION

It will be readily understood that the components of certain example embodiments, as generally described and illustrated in the figures herein, may be arranged and designed in a wide variety of different configurations. Thus, the following detailed description of some example embodiments related to laterally moveable compressor piston rod lip seals is not intended to limit the scope of certain example embodiments, but is instead representative of selected example embodiments.

In the field of compressor packings, “packing” generally refers to components that are packed around a shaft and held in place to provide a seal. Current pressure packings can include an assembly of seals and cups that seal high-pressure cylinder gas, and divert any leakage into a vent gas system for disposal or further processing. In general, a pressure packing can include a dynamic pressure breaker, at least three high-pressure packing ring sets (i.e., seals), and a vent ring set, all of which are housed in cups within the assembly. While the cups can be metallic, the sealing elements can be made of a filled polymer (e.g., carbon black, graphite fiber, metal particles, metal oxide particles) in order to improve flexibility, chemical resistance, and anti-wear properties. Furthermore, a gasket may form a seal between the pressure packing and the crank-end or head-end head, while a flange with bolts can secure the entire pressure packing in place.

A dynamic pressure breaker may include an orifice that restricts the flow of dynamic gas pressure (i.e., difference between suction pressure and discharge pressure) into the pressure packing, thereby reducing the pressure from discharge down to approximately the suction pressure. Pressure breakers generally have three segments around the piston rod that are held together, and in contact with, the piston rod via a spring on the outer diameter. When installed on the piston rod, gaps between segments between the piston rod and the packing cup can form the orifice.

A pressure packing may include at least three high-pressure packing ring sets, which may serve as the main gas seals. In general, only one packing ring set may form the seal from approximately suction pressure down to atmosphere, while addition packing ring sets can be used for additional longevity. Each packing ring set may include three or four individual rings, where the first two individual sealing rings are segmented, and when combined, may create a seal. The third and/or fourth individual sealing rings may be segmented or solid, and can be used either as a seal or as structural support. Each individual ring may only be capable of providing a reliable seal when combined into a ring set. While dynamically operating, gas leakage rates through the high-pressure packing ring sets can be between 5 to 45 standard cubic feet per hour (SCFH), which can be measured using a flow meter.

Depending on the combination of individual rings in a set, the set may or may not be able to form a seal statically while the compressor is not operating. A separate static seal may be included in the pressure packing if the compressor needs to contain high-pressure cylinder gas in the absence of reciprocating piston rod motion. Static seals may be actuated by auxiliary gas pressure to perform on-demand. However, this type of static seal is complicated to operate, unreliable, and has limited longevity.

Low-pressure gas leakage through the pressure packing may be sealed by a single vent ring set, and diverted into a vent gas system. Since gas pressure at the vent ring is relatively low, and friction of the vent ring set with the piston rod is relatively high, an axial preload from a wedge, coil springs, or a wave spring may be required to prevent the ring set from shuttling in the groove and leaking. The vent ring set may include two individual segmented sealing rings that, when combined with the axial preload, can form a seal.

Dynamic pressure breakers and high-pressure packing ring sets may need to be in contact with the piston rod and packing cup to be ready to energize and form a seal. Radial contact with the piston rod and circumferential (i.e., tangential) contact between the sealing segments may be created by a spring on the outer diameter, while intermittent axial contact between individual rings and the cup may be created via reciprocating piston rod motion. High-pressure cylinder gas may energize the dynamic pressure breaker and high-pressure packing ring sets in the radial, circumferential, and axial directions in order to form a seal. Vent ring sets may be held in radial contact with the piston rod, and circumferential contact between the sealing segments. The vent ring sets may be energized by a spring on the outer diameter, while also being held in axial contact with the cup, and energized by an axial preload from a wedge, coil springs, or a wave spring.

High-pressure packing ring sets may be broken into two types: segmented rings, and a hybrid combination of segmented and solid rings. Segmented rings may use three individual rings in a set. The first individual ring may be segmented into three pieces around the piston rod with radial gaps, and may be held together with a spring on the outer diameter. The radial gaps in the first individual ring may allow gas to flow into the cup and on top of the ring set for energization, and to vent back to the cylinder when not needed. Oil injected into a lubricated packing may pass through the vented path into the cylinder. The second individual ring may be segmented into three pieces with partial radial gaps that transition to a tangential cut, and may be held together with a spring on the outer diameter. The first two individual rings may be pegged together to phase the radial gaps, and may be the minimum combination of individual rings capable of forming a seal. The third individual ring may be segmented into three radial pieces without gaps between segments, may have clearance of the piston rod, may provide structural support, and may continue the seal formed by the first two individual rings (but may be incapable of forming the seal itself). The third individual ring may contact the piston rod, and hang from gravity. Specifically, the third individual ring may only be in contact with the piston rod at a single point by the ring pulled down by gravity; the third individual ring may be metallic, and without sufficient lubricant, can result in significant damage when in contact with the metal piston rod. Since many segments may be individually manufactured and assembled to form a seal, inherent leak paths may exist through which gas may escape the seal. In addition, segments may thermally develop from radial contact with the piston rod and/or circumferential (i.e., tangential) contact between segments, resulting in a loss of seal function. Segmented rings may also be relatively expensive to manufacture.

Furthermore, segmented rings may self-adjust after significant wear on the inner diameter of the sealing segments, thereby increasing longevity. Segmented rings were initially constructed with materials having high wear rates, and needed to meet the requirements for life expectations of compressor operators. Segmented rings also were mandated by American Petroleum Institute (API) standards such that packing rings could be installed with the piston rod still intact. However, many compressors can be difficult to maintain, and may need packing ring sets that can be installed with the piston rod intact. Other compressors have piston rods that may not be inserted through solid seals.

As noted above, high-pressure packing ring sets may include a second type with a hybrid combination of segmented and solid rings. In general, a hybrid combination may use four individual rings in a set. The first and second individual rings may be segmented, as discussed above, and may be capable of forming a seal. The third individual ring may be solid, radially and/or circumferentially rigid, and axially flexible, which may require clearance on the inner diameter for insertion of the piston rod. With the first two individual rings energized, radial and axial differential pressure may be created across the third individual ring, which, when high enough, may force the ring to collapse radially, and dish axially into sealing contact of the leading edge with the piston rod, which may result in the seal of the first two rings to break. The fourth individual ring may be solid with clearance over the piston rod, may provide structural support, and may continue the seal formed by the first three rings, but may be unable to form a seal by itself. The fourth individual ring may contact the piston rod and hang from gravity. Thus, this type of packing ring set may be a hybrid of segmented and solid seals since the third solid ring may rely on the first two segmented rings to move the radial and circumferential sealing edge/surface of the third solid ring into contact with the piston rod and to energize. When energized at a high enough pressure, this type of solid ring seal may not have inherent leak paths, as well as lower gas leakage rates and heat generation, but may have very low wear volume compared to segmented packing rings. Although this solid sealing ring is larger, only a few thousandths of an inch of the leading edge may be consumed by wear before a loss of function occurs. The solid sealing ring may also wear rapidly from excessive dishing, resulting in a loss of seal function and failure. Low wear volume may also reduce longevity.

In a lubricated application, individual structural rings may be metallic to improve anti-extrusion resistance at high pressures, revolutions per minute (RPMs), and temperatures. In an oil-free application, this ring may be made of a filled polymer to minimize wear from contact with the reciprocating piston rod. Filled polymers may not be as strong as metallic materials, which may necessitate a reduction in operating pressure, RPM, and temperature in oil-free applications.

Radial clearance may exist in the drive train between crosshead shoes and the slide bore in the crosshead guide, as well as between the outer diameter of the piston and the cylinder bore. Forces exerted on the crosshead from the connecting rod may cause the crosshead to move up and down within clearances. Uneven compression across the face of the piston may also cause the piston to rock, which may result in bending of the attached piston rod. With the assembly clearances, excitations of the crosshead and piston, and the dynamic nature of operating a reciprocating compressor, some amount of lateral piston rod motion (e.g., perpendicular to the axis of the piston rod) may occur during operation. Lateral piston rod motion may move the sealing segments out of radial contact with the piston rod, providing opportunities for gas to leak or compress the sealing elements radially into the cup and beyond their structural limit, providing additional failure and leakage. All sealing elements in the pressure or wiper packing may thus be capable of moving within the cup with the lateral motion of the piston rod in order to maintain a seal with the piston rod.

Current wiper packings may include an assembly of seals and cups that wipe lubricant oil from the piston rod, transfer the oil back to the crankcase, and prevent any cylinder gas from leaking into the crankcase. In general, a wiper packing may include an oil wiper ring set and a vent ring set, which may be housed in cups within the assembly. Oil wiper ring sets may use segmented rings, which may be similar to the segmented seals described above, although the oil wiper rings may be configured to transfer oil. Individual wiping rings may have two wiping lands on the inner diameter, as well as multiple drainage slots and holes to transfer oil radially away from the piston rod. Segmented oil wipers may transfer the bulk of the lubricant oil from the piston rod back to the crankcase, but also leak a significant amount of oil. The wiping and sealing elements may be made of a filled polymer, while the cups may be metallic. Bolts may secure the entire wiper packing assembly in place near the crankcase.

Packing ring and oil wiper sets may be housed in cups for functionality; however, since the cups may have a significantly longer lifespan than the packing rings and oil wiper sets, the ring sets may be available without cups for maintenance. When worn out, metal packing cups may be re-machined during maintenance to satisfy new specifications, but packing ring and oil wiper sets may be disposed, and new ring sets required.

Certain example embodiments described herein may have various benefits and/or advantages to overcome the disadvantages described above. For example, certain example embodiments may provide near-zero gas leakage rate, which may be significantly lower than segmented rings or a hybrid of segmented and solid rings. Some example embodiments may also reduce greenhouse gas emissions, and may not rely on other technologies to maintain contact with the sealing surfaces prior to energization. In addition, various example embodiments may maintain near-zero leakage rates at most operating design pressures, temperatures, and speeds, including at zero RPM. Certain example embodiments may also distribute pressure across multiple seals during or after operation, and may not require additional hardware or systems to maintain near-zero leakage after the compressor is shutdown to restarted. Furthermore, some example embodiments may provide higher pressure, speed, and temperature operation in an oil-free compressor. Various example embodiments may also lower oil consumption for lubricated applications. Some example embodiments may be configured for any diameter piston rod. In addition, certain example embodiments may be housed in a cylinder in conjunction with a piston seal.

Certain example embodiments may be more capable of building a hydrodynamic oil film during operation for additional load carrying, and may wipe more oil from the piston rod compared to traditional segmented oil wipers. In some example embodiments, more wear volume may be achieved compared to solid sealing rings with a hybrid of segmented and solid rings, lower heat generation than segmented rings alone, and improved heat transfer from the lip seal through the carrier to the cup assembly. In addition, various example embodiments may experience fewer failure modes, may have longer lifespans, may require fewer seals to achieve the same performance, and be less expensive.

Packing ring sets may need to conform with API 618 mandate requiring packing ring sets to be designed for installation with a piston rod in place. Some existing compressors are difficult to maintain, and may require packing ring sets that may be installed with the piston rod in place. Some existing packing ring sets may also rely on multi-part assemblies to enable all of the rings and springs of the packing ring sets to be installed with the piston rod in place. In contrast, various example embodiments described herein include packing ring sets that may be installed with the piston rod removed.

Various example embodiments discussed herein also provide more wear volume that a solid sealing ring. When coupled with polymer materials, lubricants, piston rod coatings, and lip seal designs, only a small amount of wear may occur to meet the longevity goals of compressor operators.

Furthermore, lip seals may fail prematurely when used in a laterally fixed configuration on a reciprocating shaft with lateral motion. The use of a laterally-movable seal carrier may add another leak path between the carrier and the cup face, which may not provide a secure sealing solution; such an additional leak path may be where a quasi-static seal can be made, which may provide a near-zero leakage compared to traditional dynamic seals.

In certain example embodiments, a reciprocating gas compressor may include a piston rod sealing assembly with high-pressure cylinder gas at an annular opening between the piston rod and a crank-end or head-end cylinder head. The piston rod sealing assembly may include a dynamic pressure breaker, at least two main seals and a vent seal, with each housed in its own cup to loosely constrain its axial position within the assembly. The dynamic pressure breaker may reduce the pressure from discharge down to approximately suction pressure. The vent seal may capture leakage past the main seals, and instead force any leakage into a vent gas system for disposal or further processing. A laterally moveable compressor piston rod lip seal assembly may serve as the main seal, and may reduce the pressure in the piston rod sealing assembly from approximately suction pressure down to atmosphere. Some example embodiments may also seal discharge pressure down to atmosphere if a dynamic pressure breaker is omitted from the assembly. Lip seals may be made of a filled polymer to improve flexibility, chemical resistance, and anti-wear properties. Various example embodiments may also produce near-zero gas leakage, consume minimal quantities of lubrication and provide increased longevity.

Some example embodiments may include a separate seal carrier for operating conditions that require the seal carrier so as to provide greater strength or stiffness with the use of a higher duty polymer, composite, or metal, or an integrated seal carrier if operation conditions would otherwise allow the seal carrier to be made of the same filled polymer as the lip seal. Some separate seal carriers may be configured with a notch to vent gas to a cylinder, if the gas is not needed to form a seal. Also, some configurations with a separate seal carrier may have a peg between the seal carrier and the lip seal to prevent relative rotation if relative rotation would increase wear. If configured with a separate seal carrier, the heel of the lip seal may be inserted into a generally metallic seal carrier, and force may be applied until it snaps into place. A barb in the seal carrier may secure the lip seal axially by the outer lip. The seal carrier may be solid and have clearance over the piston rod. Further, the seal carrier may have a pilot diameter for a wave spring. In addition, some example embodiments may each be housed in individual cups and assembled with the remainder of the piston rod sealing assembly. Further, some example embodiments may have a lip seal with circumferential lip including a plurality of points of contact to improve seal strength. A gasket may form a seal between the piston rod sealing assembly and the head while a flange with bolts may hold the entire assembly in place. Some example embodiments may be installed with the piston rod removed since some compressors may require minimal maintenance. The piston rod may then be inserted through the piston rod sealing assembly.

In certain example embodiments, sealing surfaces may be in radial, circumferential, and/or axial contact in order to properly energize and form a seal. All sealing surfaces may be in contact with each other to form a seal. For example, a lip seal may be radially and circumferential flexible, but axially stiff. When the piston rod is installed, the lips may be secured with the piston rod, the seal carrier may be secured with radial and circumferential interfering geometry, and radial force from the canted coil spring, with no additional requirements to energize in the radial and circumferential directions. At least one barb in the seal carrier may retain the lip seal axially, thereby securing the lip seal in the seal carrier while the piston rod may reciprocate without seal energization in the axial direction. Reciprocating piston rod motion may place the seal carrier face into intermittent axial contact with the cup face.

In various example embodiments, a seal may be formed (i.e., energized) or maintained when the contact pressure between sealing surfaces may be equal to or greater than the differential pressure being contained. Static seals may have a lower leakage than dynamic seals since there may be no motion between sealing surfaces. Dynamic seals may have more leakage compared to static seals since the motion between sealing surfaces with imperfections may allow more leakage through such imperfections. Leakage along surfaces with imperfections may be reduced with increased contact pressure. Lip seals may have zero or near-zero leakage due to no inherent leak paths through the solid seal technology.

Various example embodiments may include formed seals (e.g., while energized) with the seals being maintained by high-pressure cylinder gas in the radial, circumferential, and/or axial directions, with the assistance in the radial direction by forces from a canted coil spring between the lips of the seal. Inner lips of the seal may form a dynamic seal with the piston rod, while outer lips may form a static seal with the seal carrier (if applicable). While the heel of the lip seal may exert force on the seal carrier, contacting faces may not form a primary seal. The face of the seal carrier (e.g., separate or integral) may form a quasi-static seal with the cup face. Thus, a seal formed between the carrier and the cup face may be static, except for minimal displacement lateral motion (i.e., perpendicular to the axis of the piston rod) that may be driven by the piston rod. The laterally moveable seal carrier may allow the inner lip seal to move along with lateral motion of the piston rod in order to maintain the seals. Thus, the laterally moveable seal carrier may enable lip seals to be applied in reciprocating gas compressors.

As noted above, lip seals may provide consistent, near-zero leakage rates. Since lip seals may form a tight and consistent seal, multiple seals may be used in the piston rod sealing assembly to share the pressure. Such pressure sharing may allow operation at pressures higher than what an individual seal is capable of, and/or may increase longevity by reducing the load on each seal.

So long as cylinder pressure is continuously applied to the piston rod sealing assembly, various example embodiments may maintain near-zero leakage rates, and/or may share pressure across multiple embodiments after the compressor stops rotating. Thus, various example embodiments may maintain near-zero leakage rates while the compressor is re-started without depressurizing the cylinder.

In order to improve optimum performance in a lubricated application, oil may be injected between a minimum of two lip seals. Certain example embodiments may prevent gas and oil from leaking to low-pressure vent locations, while also sealing gas and oil from venting to the cylinder. Trapping oil between lip seals may result in high oil levels in the piston rod sealing assembly, which in turn may result in low heat generation, low wear rates, and increased longevity. The natural retention of oil between lip seals may not require significant oil to maintain a consistently high level. The shape of the lips and/or the radially/circumferentially flexible nature of the design of the lip seals may increase hydrodynamic oil film pressure between the reciprocating piston rod and the inner lip to add load carrying capacity.

In some example embodiments, the concentric geometry of the lip seal as installed in the seal carrier may center the seal carrier with clearance around the piston rod. Since a metallic seal carrier may not be in contact with the piston rod, and a filled polymer may generate less frictional heat compared to a metallic seal carrier, the configuration of the lip seals may result in less heat generation, require less oil, and may allow for higher pressure, RPMs, and temperature operation in oil-free applications.

Furthermore, the clearance between the seal carrier and piston rod may create an extrusion gap. At pressure and temperatures exceeding certain thresholds, the heel of the lip seal may begin to extrude from differential pressure into the clearance. A solid anti-extrusion ring made from a higher duty material may be installed in the heel of the lip seal and cover the extrusion gap in order to delay extrusion of the heel until more extreme operating conditions.

Frictional heat may be generated by the reciprocating motion of the piston rod against an inner lip. Heat may then be transferred through a lip seal radially and axially to the seal carrier, and then into the cup face. A metallic seal carrier may provide an efficient thermal path around the outer lip, and behind the heel of the lip seal for heat transfer into the cup. Since differential pressure multiplexed by the contact area between the seal and the piston rod may determine the normal force, lower frictional forces may occur by minimizing the axial length of contact between the seal and the piston rod.

Since the lip seal may be radially and circumferentially flexible, the lip seal may flex to adjust for radial wear of the inner lip to maintain sealing functions. Tens of thousands of an inch of the inner lip may be consumed from wear. Although the lip seal may appear smaller in overall size than a solid sealing ring in hybrid technology, the lip seal may have many times more wear volume, which may contribute to its longevity.

Some primary failure modes of segmented and hybrid packing ring technology may be minimized or eliminated by certain example embodiments described herein. Since there are no segments in a lip seal, there is a reduced risk of failure due to thermal expansion of segments growing out of sealing contact with the piston rod or other segments, resulting in a loss of sealing function. Since the stiffness of a lip seal is radially and circumferentially flexible, and axially stiff, the lip seal may not fail from dishing and/or rapid wear resulting in a loss of sealing function.

Various example embodiments may be configured in a piston rod oil seal assembly next to the crankcase. The piston rod oil seal assembly may include an oil seal and a vent seal, each housed in its own cup to loosely constrain its axial position within the assembly. Certain example embodiments may wipe lubricant oil on the piston rod in the circumferential and axial directions, transfer oil radially away from the piston rod and back to the crankcase, and produce near-zero oil leakage. Some example embodiments may experience small displacement reciprocating motion in the cup. The vent seal may stop any cylinder gas leakage past the piston rod sealing assembly from entering the crankcase. Various example embodiments may also be used as both an oil seal and a vent seal when an axial preload is applied.

FIGS. 1A-1F illustrate a first example embodiment of a piston rod lip seal assembly. In particular, FIG. 1A illustrates a perspective view of a first example embodiment; FIG. 1B illustrates another perspective view of the first example embodiment; FIG. 1C illustrates a rear view of the first example embodiment; FIG. 1D illustrates a left-side cross-section view of the first example embodiment; FIG. 1E illustrates a left-side view of the first example embodiment; and FIG. 1F illustrates a front view of the first example embodiment.

FIG. 1D illustrates the elements of an example embodiment of a piston rod lip seal assembly 100 with integrated seal carrier 101. The heel of integrated seal carrier 102 may create a face to seal with a cup (not shown). Canted coil spring 106 may be disposed between inner circumferential sealing lip 104 and circumferential outer ring 105. An inner diameter of wave spring 107 may fit around wave spring pilot diameter 103, and may be in face contact with circumferential outer ring 105. The other side of wave spring 107 may be in face contact with the cup.

FIGS. 2A-2F depict variations of the first example embodiment shown in FIGS. 1A-1F with slots. Specifically, FIG. 2A illustrates a perspective view of the first example embodiment with slots, FIG. 2B illustrates another perspective view of the first example embodiment with slots, FIG. 2C illustrates a rear view of the first example embodiment with slots, FIG. 2D illustrates a left-side cross-section view of the first example embodiment with slots, FIG. 2E illustrates a left-side view of the first example embodiment with slots, and FIG. 2F illustrates a front view of the first example embodiment with slots.

FIG. 2C depicts slot 201 from a rear view, FIG. 2D depicts slot 202 in a left-side cross-section view, and FIG. 2E depicts slot 203 from a left-side view. Slots 201, 202, and 203 may be similar, and may be configured to transfer oil radially away from the piston rod. FIG. 2D further depicts a plurality of points of contact 204 at an inner circumferential sealing lip of piston rod lip seal assembly 200.

FIGS. 3A-3E depict a second example embodiment of a piston rod lip seal assembly. In particular, FIG. 3A illustrates a perspective view of a second example embodiment, FIG. 3B illustrates a rear view of the second example embodiment, FIG. 3C illustrates a left-side cross-section view of the second example embodiment, FIG. 3D illustrates a left-side view of the second example embodiment, and FIG. 3E illustrates a front view of the second example embodiment.

FIG. 3C illustrates the elements of an example embodiment of piston rod lip seal assembly 300 with separate seal carrier. Lip seal 301 may be disposed inside a separate seal carrier 304. Lip seal 301 may further include canted coil spring 307, which may be disposed between both inner circumferential sealing lip 308 and outer circumferential sealing lip 305. Lip seal 301 may be retained axially in seal carrier 304 by a barb in carrier 306, such that heel 303 of lip seal 301 is in face contact with seal carrier 304. Seal carrier 304 may have sealing face 302 that forms a seal with a cup (not shown). Seal carrier 304 may also include a pilot diameter 309 for a wave spring.

FIGS. 4A-4E depict variations of the second example embodiment shown in FIGS. 3A-3E with an anti-extrusion ring. Specifically, FIG. 4A illustrates a perspective view of a third example embodiment, FIG. 4B illustrates a rear view of the third example embodiment, FIG. 4C illustrates a left-side cross-section view of the third example embodiment, FIG. 4D illustrates a left-side view of the third example embodiment, and FIG. 4E illustrates a front view of the third example embodiment.

FIG. 4C illustrates piston rod lip seal assembly 400 with anti-extrusion ring 401 being disposed inside a notch in heel 402 of the lip seal. FIG. 4C further depicts peg 404 that may prevent relative rotation between the lip seal and the seal carrier, and a notch in the seal carrier 403 configured to vent gas to a cylinder.

The features, structures, or characteristics of example embodiments described throughout this specification may be combined in any suitable manner in one or more example embodiments. For example, the usage of the phrases “various embodiments,” “certain embodiments,” “some embodiments,” or other similar language throughout this specification refers to the fact that a particular feature, structure, or characteristic described in connection with an example embodiment may be included in at least one example embodiment. Thus, appearances of the phrases “in various embodiments,” “in certain embodiments,” “in some embodiments,” or other similar language throughout this specification does not necessarily all refer to the same group of example embodiments, and the described features, structures, or characteristics may be combined in any suitable manner in one or more example embodiments.

As used herein, “at least one of the following: <a list of two or more elements>” and “at least one of <a list of two or more elements>” and similar wording, where the list of two or more elements are joined by “and” or “or,” mean at least any one of the elements, or at least any two or more of the elements, or at least all the elements.

Additionally, if desired, the different functions or procedures discussed above may be performed in a different order and/or concurrently with each other. Furthermore, if desired, one or more of the described functions or procedures may be optional or may be combined. As such, the description above should be considered as illustrative of the principles and teachings of certain example embodiments, and not in limitation thereof.

One having ordinary skill in the art will readily understand that the example embodiments discussed above may be practiced with procedures in a different order, and/or with hardware elements in configurations which are different than those which are disclosed. Therefore, although some embodiments have been described based upon these example embodiments, it would be apparent to those of skill in the art that certain modifications, variations, and alternative constructions would be apparent, while remaining within the spirit and scope of the example embodiments.

LATERALLY MOVEABLE COMPRESSOR PISTON ROD LIP SEAL ASSEMBLY

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