EP4230870A1 - Schraubenkompressor mit nebenschlussverstärkter verdichtung und pulsationsfalle (secapt) - Google Patents

Schraubenkompressor mit nebenschlussverstärkter verdichtung und pulsationsfalle (secapt) Download PDF

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Publication number
EP4230870A1
EP4230870A1 EP22157685.3A EP22157685A EP4230870A1 EP 4230870 A1 EP4230870 A1 EP 4230870A1 EP 22157685 A EP22157685 A EP 22157685A EP 4230870 A1 EP4230870 A1 EP 4230870A1
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EP
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Prior art keywords
compression
flow
nozzle
secapt
discharge port
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EP22157685.3A
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English (en)
French (fr)
Inventor
Paul Xiubao Huang
Sean William Yonkers
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Individual
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Priority to EP22157685.3A priority Critical patent/EP4230870A1/de
Publication of EP4230870A1 publication Critical patent/EP4230870A1/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/082—Details specially related to intermeshing engagement type pumps
    • F04C18/086—Carter
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F04C29/061—Silencers using overlapping frequencies, e.g. Helmholtz resonators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F04C29/068—Silencing the silencing means being arranged inside the pump housing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/126—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with radially from the rotor body extending elements, not necessarily co-operating with corresponding recesses in the other rotor, e.g. lobes, Roots type

Definitions

  • the present invention relates generally to the field of rotarygas compressors, and more particularly relates to rotary screwcompressors having twin meshing helical-shaped multi-lobe rotors.
  • a rotary screw compressor uses two helical screws, known as rotors, to compress the gas.
  • a pair of timing gears ensures that the male and female rotors each maintain precise positions and clearances.
  • injected lubricating oil film fills the space between the rotors, both providing a hydraulic seal and transferring mechanical energy between the driving and driven rotor.
  • Gas enters at the suction port of the compressor and gets trapped betweenmoving threads and compressor casingforming a series of moving cavities as the screws rotate. Then the volumes of the moving cavities decrease and the gas is compressed.
  • the gas exits at the end of the screw compressor through a discharge portnormally connected to a discharge dampener to finish the cycle. It is essentially a positive displacement mechanism but using rotary screws instead of reciprocating motion so that displacement speed can be much higher. The result is a more continuous stream of flow with a more compact size whencomparing with the traditional reciprocating types.
  • the range of the pressure ratio variation is significantand the effects of OC and UC are further enhanced by the elevated pressures that refrigerant needs to operate.
  • Another example of requiring a wide range of operating pressure ratios is the vacuum pump that is used to pull down the vacuum level in a system (for example, to pump air from a vessel to atmosphere), continuously increasing the pressure ratio as the vacuum level gets higher and higher.
  • the UC and OC inducedenergy losses and gas pulsations are significant, especially the later one, if left undampened, can potentially damage downstream pipelines, equipment and induce severe vibrations and noise within the compressor system.
  • a large pulsation dampener known in the trade as reactive and/or absorptive type as shown in Figure 2a is usually required at the discharge side of a screw compressor to dampen the gas pulsations and induced NVH. It is generally very effective in gas pulsation control with a reduction of 20-40 dB but is large in size and causes other problems such as inducing more noises due to additional vibrating surfaces, orsometimes causes dampener structure fatigue failures that couldresult in catastrophic damages to downstream components and equipment.
  • discharge dampeners used today create high pressure losses as illustrated in Figure 2b that contribute to poor compressor overall efficiency. For this reason, screw compressors are often cited unfavorably with high gas pulsations, high NVHand low off-design efficiency and bulky size when compared with dynamic types like the centrifugal compressor.
  • slide valve To overcome the mismatch problem at source, a concept called slide valve has been explored widely since 1960s as demonstrated in Figures 3a-3b .
  • the slide valve concepts are disclosed in US Patent number 3,088,659 to H. R. Nilsson et al and entitled “Means for Regulating Helical Rotary Piston Engine” 4,215,977 , or in US Patent number 3,936,239 to David. N. Shaw and entitled "Under-compression and Over-compression Free Helical Screw Rotary Compressor".
  • variable Vi scheme is to use a slide valve to mechanically vary the internal volume ratio hence compression ratio of the compressor to meet different operating pressure requirements, andto eliminate the under-compression and/or over-compression that are the source of discharge gas pulsations and energy losses.
  • these systems typically are very complicated structurally with high cost and low reliability. Moreover, they do not work well for widely used dry screw applications where lubrication is essential between sliding parts.
  • a shunt pulsation trap (SPT) technology as shown in Figures 4a-4b was disclosed for example in several co-owned patents ( U.S. Patents Nos. 9,140, 260 ; 9,155,292 ; 9,140,261 ; 9,243,557 ; 9,555,342 ; and 9,732,754 ).
  • the idea is to use fluidly gas to compensate the variable load conditions rather than moving the solidly mechanical parts that are sensitive to friction, fatigue failure and response frequency.
  • SPT is capable of achieving the same goal of the slide valve by an automatic feedback flow loop both to communicate between the compressor cavity and outlet (discharge port) and to compensate the cavitycompression by adding or subtracting gases (just like inflating or deflating a basketball) in such a way as to eliminate the under-compression or over-compression when discharge port opens.
  • Conventional SPT technology is effective in under-compression mode for suppressing low-frequency pressure pulsation levels and reducing energy consumption by the elimination of back-pressure loss inherent with serial dampening. However, it does not work well in over-compression mode, especially for screw compressorsoperating over a wide range of pressure ratios.
  • the present invention relates to a shunt enhanced compression and pulsation trap (SECAPT) for screw compressor having a compression chamber with a suction port and a discharge port, and a pair of multi-helical-lobe rotors housed in the compression chamber forming a series of moving cavities for trapping, compressing and propelling the trapped gas in the cavities from the suction port to discharge port.
  • SECAPT comprises an inner casing as an integral part of the compression chamber, and an outer casing surrounding part of the inner casing near the discharge port forming at least one diffusing chamber, therein housed at least one feedback flow loop through at least one flow nozzle (located at one of the moving cavities at least one male lobe span away or totally isolated from the suction port) to communicate between the propelled moving cavities and the discharge port.
  • the SECAPT automatically compensatescavity pressure, in a similar way as inflating or deflating a basketball by adding or subtracting gas to the cavity, to meet different outlet pressures (hence eliminating the under-compression and/or over-compression when the discharge port opens), partially recovers the potential energy associated with the under-compression (UC), and traps and attenuates gas pulsations and noise before the discharge port opens.
  • FIG. 5 is a flow chart of a screw compression cycle with the addition of a shunt enhanced compression and pulsation trap (SECAPT) according to example embodiments of the present invention, linking the internal compression phase to the discharge pressure.
  • SECAPT shunt enhanced compression and pulsation trap
  • IC internal compression
  • SECAPT is used to assist internal compression (IC), to trap and attenuate gas pulsations and noises, and to improve off-design efficiency, without using a slide valve and/or a traditional serial pulsation dampener.
  • a SECAPT involves modifications to a standard screw compression cycle from a serial mode, that is, from internal compression and dampening in series as shown in the prior art of Figure 2a , to a parallel mode where IC and SECAPT are carried out simultaneously and synergistically during a much longer time interval.
  • any UC or OC pressure deficit or build-up at the compressor discharge will be minimized so that there would be no need to use a downstream dampener (However, an optional absorptive silencer could be used if flow induced broadband noise needs to be attenuated, say for vacuum applications when gas is discharged to atmosphere).
  • FIGS.6 ato 6c there is shown a typical arrangement of a screw compressor10 with a shunt enhanced compression and pulsation trap (SECAPT)apparatus 50 according to a first example embodiment.
  • the screw compressor10 has two rotors 12integrated withtwo rotor shafts 11,respectively, where rotor shaft11 is driven by an external rotational driving mechanism (not shown).
  • the rotors 12 are typically driven through a set of timing gears (in case of dry running)or they drive each other directly (for oil injected case).
  • the twin rotors 12 are typically a pair ofmulti-helical-lobe rotors, one male and one female, housed in the compression chamber 32 forming a series of moving cavities such as 38 and 39 for trapping, compressing, and propelling the trapped gas in the cavities 38 and 39 from a suction port 36 to a discharge port 37of the compressor 10.
  • the screw compressor10 also has an inner casing 20 as an integral part of the compression chamber32, wherein rotor shafts 11 are mounted on an internal bearing support structure (not shown).
  • the casing structure further includes an outer casing 28 surrounding part of the inner casing 20 near the discharge port 37 forming at least one diffusing chamber 55.
  • a SECAPT apparatus 50 is comprised of at least one flow nozzle (trap inlet) 51 branching off from the compression chamber32 into at least onediffusing chamber55 and a feedback region(trap outlet) 58 communicating with the compressor outlet 37.
  • the starting line of the flow nozzle (trap inlet) 51 is located at one of the moving cavities 38 or 39 at least one lobe span (or a screw pitch t) away from the suction port 36 closing line and positioned as far away (distance d on FIG.
  • FIG. 6b also shows two types of flow nozzles 51 used: on the left is a 2D nozzle with rectangular cross-sectional shape with a converging cross-sectional area distribution along the axis; and on the right are two 3D nozzles with circular cross-sectional shape with a converging cross-sectional area distribution along the axis.
  • Fig.6a shows the flow pattern for an under-compression mode where the large directional arrows30 show the direction of thecavity flow as propelled by the rotors 12 from the suction port 36 to the discharge port 37 of the compressor 10, while feedback flow IFF 53 as indicated by the small directional arrows goes from the feedback region (trap outlet) 58through the diffusing chamber55, then converging to the flownozzle (trap inlet) 51and releasing into the cavity 39 that is open to the flow nozzle 51.
  • Fig.6c shows the flow pattern for an over-compression mode where the large directional arrows 30 still show the direction of the cavity flow as propelled by the rotors 12 from the suction port 36 to the discharge port 37 of the compressor 10, while feedback flow IFF 54 as indicated by the small arrows goes from the cavity 39 that is now opened to the flow nozzle 51through the diffusing chamber 55, and releasing into the trap outlet 58 that merges with the discharge flow 30.
  • the SECAPT apparatus50 of the present invention When a screw compressor10 is equipped with the SECAPT apparatus50 of the present invention, there exist both a reduction in the gas pulsation and induced noises transmitted from screw compressoroutletto downstream flow as well as an improvement in internal flow field (hence its adiabatic off-design efficiency) for under-compression and/or over-compression operations.
  • the theory of operation underlying the SECAPT apparatus50 of the present invention can be described as follows. As illustrated in FIGS.6a and 6b for an under-compression mode, the SECAPT is designed to assist theinternal compression from themomentwhen the gas pressure of cavity 39 reaches a minimum Pi(but far below the maximum) operating pressure of an application.
  • the required mass is more efficiently transported using a nozzle 51 into the "starved" or under-compressed cavity 39 to minimize fill-in time and pulsation generation at discharge. It can be seen that the required mass flow 53 is first “borrowed” from the outlet area 37 and then “returned” to the outlet area 37 by a shunt feedback flow loop as shown in FIG. 5 so that the induced flow 53 is not lost in the process.
  • the amount of the feedback flow53 is designed to compensate the internal compression before discharge in such a way that the pressure difference ⁇ P UC or ⁇ P OC would be eliminated or reduced close to nearly zero at discharge as shown in FIG. 5 .
  • the speed of the jet flow at the nozzle throat can be close or equal to the speed of sound for high ⁇ P UC , much faster than the speed of moving cavity 39, it is possible for the scheme to work for high speed dry screw compressors where variable Vi design does not work well.
  • a nozzle 51as a trap would isolate the high velocity jet noises inside the cavity 39 before discharging as long as the nozzle throat 51 is choked so that no CW and jet induced sound could escape or propagate upstream through the nozzle throat 51.
  • the CW and jet noises inside the cavity 39 will be reduced greatly due to very small throat area for the noise to escape out.
  • the SECAPT apparatus50 for an over-compression mode is different.
  • the SECAPT is designed to assist the internal compression from the moment when the gas pressure P 1 of cavity 39 is slightly over the minimum operating pressure P 2 at the outlet 37of the compressor 10 of an application.
  • more than one nozzle can be used to feed both male and female sides of the cavity 39, and/or the nozzle/s can optionally be in the form of circular hole (3-dimensional nozzle) or slot (2-dimensional nozzle) arranged in parallel with the lobe seal line of the cavity 39 (for illustration purposes, both are shown in FIG. 6b ).
  • the throat 59 cross section can be designed to be circular/non-transitioned ( FIG.
  • FIG. 7a or gradually transitioned to a slot shape into the cavity 39 and oriented generally along the cavity longer side which is parallel with the lobeseal line of the cavity 39either with the same cross sectional area as the nozzle throat 59 ( FIG. 7b ) or with a gradually increased cross-sectional area resulting in so called de Laval nozzle ( FIG.7c ).
  • Replacing a circular cross-sectional shape ( FIG. 7a ) with a slot as shown in FIGS. 7b and 7c will alsoreduce the stage spacing defined as perpendicular to the rotor sealing line, hence gaining more timing for the second stage operation.
  • slot shape would help flow exchange of the oblong shaped cavity 39 with the diffusing chamber 55, and improve the efficiency of the feed-in flow 53 for under-compression or the feed-out flow 54 for over-compression condition, especially for high speed dry screw application.
  • a one-stage SECAPT is enough to cover the compounded compression phase when the distance between the nozzle 51 opening to discharge port 37 opening is smaller than one lobe span or screw pitch t as shown in FIG. 6b .
  • a two-stage SECAPT can be used to cover the compounded compression phase when the distance between the closing of the first nozzle opening to the discharge port opening is the same or larger than one lobe span or screw pitch t.
  • the principle is that each cavity should always be in communication with the compressor outlet at any instant after being connected, but cavities never communicate with each other.
  • the start of the 2 nd stage nozzle should be located at leastone screw pitch t away from the end of the 1 st nozzle and within the last screw pitchbefore the discharge port opening.
  • a three-stage SECAPT can be used.
  • FIGS. 8a to 8c there is shown a typical arrangement of a two-stage SECAPT according to a second example embodiment of a screw compressor 10 with a shunt enhanced compression and pulsation trap (SECAPT) apparatus 60.
  • SECAPT shunt enhanced compression and pulsation trap
  • the construction of the screw compressor 10 and the first stage of the SECAPT apparatus 60 can be the same as for the SECAPT apparatus 50 as discussed above.
  • a second stage of SECAPT apparatus 60 is added which is further comprised of at least one flow nozzle 61 (trap inlet) branching off from the compression chamber 32 into at least one diffusing chamber 63 and connected to a feedback region (trap outlet) 68 communicating with the compressor outlet 37.
  • the first nozzle 51(trap inlet) is still located at least one lobe span (one screw pitch t) away from the suction port 36 closing line and the start of the second nozzle 61 is located at least one screw pitch t away from the closing of the first nozzle 51, both of which are positioned as far away (distance d on FIG. 8b ) from the rotating axis 11 as possible and directed at the same direction as the rotating rotor12 to assist its rotating.
  • FIG.8a shows the flow pattern for an under-compression mode for both stages where the large directional arrows 30 show the direction of the cavity flow as propelled by the rotors 12 from the suction port 36 to the discharge port 37 of the compressor 10, while feedback flows 53 and 63 as indicated by the small directional arrows goes from the feedback region (trap outlet) 58 through the diffusing chambers55 and 65, then converging to the flow nozzles51and 61 and releasing into the cavities 38 and 39 respectively.
  • FIG.8c shows the flow pattern for an over-compression mode for both stages where the large directional arrows 30 still show the direction of the cavity flow as propelled by the rotors 12 from the suction port 36 to the discharge port 37 of the compressor 10, while the feedback flows 54 and 64 as indicated by the small directional arrows go from the cavities 38 and 39 that are now opened to the nozzles51and 61 through the diffusing chambers55 and 65, and releasing into the trap outlets58and 68 that merge with the discharge flow 30.Furthermore, FIG.
  • 8d shows the flow pattern of an under-compression conditionfor the first stage and an over-compression for the second stagewhere the feedback flow 54 for the first stage goes from the feedback region (trap outlet) 58 through the diffusing chamber 55, then to the flow nozzle 51, and is then released into the cavity 38, while the feedback flow 64 for the second stage goes from the cavity 39 that is now opened to the nozzle 61, through the diffusing chamber 65, and is released into the trap outlet 68 that merge with the discharge flow 30.
  • a three-port configuration can be used for a screw vacuum pump application for pulling deep vacuum.
  • the suction port of the compressor is connected to a process or a vessel where a deep vacuum is to be created while the outlet port of the compressor is connected through a silencer to atmosphere.
  • a third port is added that is also open to atmosphere and allows cool atmospheric air into the compressor cavity through the SECAPT to extend the pressure ratio range, e.g., from about 4/1 to about 20/1 or more.
  • FIGS. 9a and 9b there are shown typical arrangements of a one-stage and a two-stage SECAPT, according to third and fourth example embodiments, respectively,of a screw compressor 10 with a shunt enhanced compression and pulsation trap (SECAPT) apparatus 70 and 80, respectively.
  • SECAPT shunt enhanced compression and pulsation trap
  • a typical mode of operation for a one-stage SECAPT 70 is first releasing flow (not shown)from the cavity 39 through the nozzle 51 then through the diffusing chambers 55 to the port 77 and into the atmosphere 78 when the operating pressure ratio is less than the design pressure ratio of the compressor 10 to get rid of the over-compression. Then the flow direction (not shown) is automatically switched to pulling cooler atmospheric air from port 77 through the diffusing chambers 55and nozzle 51 into the compressor cavity 39 when the operating pressure ratio is more than the design pressure ratio of the compressor 10.
  • the cool ambient air mixed with hotter cavity air after internal compression will allow the compressor to reach a much higher pressure ratiobeyond its normal operating range, say from about 4/1 to about 20/1 or more.
  • a screw compressor with a shunt enhanced compression and pulsation trap (SECAPT) in parallel with the compressor internal compression helps eliminate the under-compression and/or over-compression (sources of discharge gas pulsations and energy losses) when discharge port opens.
  • Ascrew compressor with a shunt enhanced compression and pulsation trap (SECAPT) can be as effective as a slide valve variable Vi design but without mechanical moving parts and limitation to oil-injected applications.
  • a screw compressor with a shunt enhanced compression and pulsation trap (SECAPT) can be an integral part of the compressor casing so that it is compact in size by eliminating the serially connected pulsation dampener at discharge.
  • a screw compressor with a shunt enhanced compression and pulsation trap can be capable of achieving energy savings over a wide range of pressure ratios.
  • a screw compressor with a shunt enhanced compression and pulsation trap can be capable of achieving reduced gas pulsations and NVH over a wide range of pressure ratios.
  • a screw compressor with a shunt enhanced compression and pulsation trap can be capable of achieving energy savings and higher gas pulsation attenuation over a wide range of speed and cavity passing frequency.
  • a screw compressor with a shunt enhanced compression and pulsation trap can be capable of achieving the same level of adiabatic off-design efficiency as a slide valve over a wide range of pressure and speed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP22157685.3A 2022-02-21 2022-02-21 Schraubenkompressor mit nebenschlussverstärkter verdichtung und pulsationsfalle (secapt) Withdrawn EP4230870A1 (de)

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EP22157685.3A EP4230870A1 (de) 2022-02-21 2022-02-21 Schraubenkompressor mit nebenschlussverstärkter verdichtung und pulsationsfalle (secapt)

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Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3088659A (en) 1960-06-17 1963-05-07 Svenska Rotor Maskiner Ab Means for regulating helical rotary piston engines
US3936239A (en) 1974-07-26 1976-02-03 Dunham-Bush, Inc. Undercompression and overcompression free helical screw rotary compressor
US4215977A (en) 1977-11-14 1980-08-05 Calspan Corporation Pulse-free blower
US9140260B2 (en) 2010-06-08 2015-09-22 Hi-Bar Blowers, Inc. Rotary lobe blower (pump) or vacuum pump with a shunt pulsation trap
US9140261B2 (en) 2011-03-14 2015-09-22 Hi-Bar Blowers, Inc. Shunt pulsation trap for cyclic positive displacement (PD) compressors
US9155292B1 (en) 2014-12-08 2015-10-13 Jeremy Nathan Tweedie Sand spike accessory apparatus
US9243557B2 (en) 2011-09-17 2016-01-26 Paul Xiubao Huang Shunt pulsation trap for positive displacement (PD) internal combustion engines (ICE)
US9555342B2 (en) 2010-05-18 2017-01-31 Envirollea Inc. Thermal processing reactor for mixtures, fabrication of the reactor, processes using the reactors and uses of the products obtained
CN106481564A (zh) * 2015-08-26 2017-03-08 黄秀保 带有旁支脉动陷阱的容积式气/汽体机械
US9732754B2 (en) 2011-06-07 2017-08-15 Hi-Bar Blowers, Inc. Shunt pulsation trap for positive-displacement machinery
EP3670916A2 (de) * 2018-12-20 2020-06-24 Ingersoll-Rand Company Vakuumpumpe mit geräuschdämpfendem durchgang

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3088659A (en) 1960-06-17 1963-05-07 Svenska Rotor Maskiner Ab Means for regulating helical rotary piston engines
US3936239A (en) 1974-07-26 1976-02-03 Dunham-Bush, Inc. Undercompression and overcompression free helical screw rotary compressor
US4215977A (en) 1977-11-14 1980-08-05 Calspan Corporation Pulse-free blower
US9555342B2 (en) 2010-05-18 2017-01-31 Envirollea Inc. Thermal processing reactor for mixtures, fabrication of the reactor, processes using the reactors and uses of the products obtained
US9140260B2 (en) 2010-06-08 2015-09-22 Hi-Bar Blowers, Inc. Rotary lobe blower (pump) or vacuum pump with a shunt pulsation trap
US9140261B2 (en) 2011-03-14 2015-09-22 Hi-Bar Blowers, Inc. Shunt pulsation trap for cyclic positive displacement (PD) compressors
US9732754B2 (en) 2011-06-07 2017-08-15 Hi-Bar Blowers, Inc. Shunt pulsation trap for positive-displacement machinery
US9243557B2 (en) 2011-09-17 2016-01-26 Paul Xiubao Huang Shunt pulsation trap for positive displacement (PD) internal combustion engines (ICE)
US9155292B1 (en) 2014-12-08 2015-10-13 Jeremy Nathan Tweedie Sand spike accessory apparatus
CN106481564A (zh) * 2015-08-26 2017-03-08 黄秀保 带有旁支脉动陷阱的容积式气/汽体机械
EP3670916A2 (de) * 2018-12-20 2020-06-24 Ingersoll-Rand Company Vakuumpumpe mit geräuschdämpfendem durchgang

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