CN102667152A - Viscoelastic compressor pulsation dampener - Google Patents
Viscoelastic compressor pulsation dampener Download PDFInfo
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- CN102667152A CN102667152A CN2010800521244A CN201080052124A CN102667152A CN 102667152 A CN102667152 A CN 102667152A CN 2010800521244 A CN2010800521244 A CN 2010800521244A CN 201080052124 A CN201080052124 A CN 201080052124A CN 102667152 A CN102667152 A CN 102667152A
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- pulsation
- damping
- process fluid
- valve assembly
- reciprocal compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0027—Pulsation and noise damping means
- F04B39/0033—Pulsation and noise damping means with encapsulations
- F04B39/0038—Pulsation and noise damping means with encapsulations of inlet or outlet channels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/02—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders arranged oppositely relative to main shaft
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0027—Pulsation and noise damping means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0027—Pulsation and noise damping means
- F04B39/0044—Pulsation and noise damping means with vibration damping supports
Abstract
A system, in certain embodiments, includes a pulsation dampener for minimizing the adverse effects of pulsation waves in a process fluid generated by a reciprocating compressor. The pulsation dampener may be installed proximate to the source of the pulsation waves and external to a main flow path of the process fluid being compressed within the reciprocating compressor. More specifically, in certain embodiments, the pulsation dampener may be a pulsation dampening valve enclosure configured to at least partially encase a valve assembly of the reciprocating compressor. The pulsation dampening valve enclosure may be filled with a pulsation dampening material, such as a wire mesh material, a viscoelastic material, an elastomeric material, or a combination thereof.
Description
The cross reference of related application: the exercise question that the application requires to submit on November 17th, 2009 is the non-temporary patent application No.12/620 of the U.S. of " viscoelasticity compressor damping of pulsation device (Viscoelastic Compressor Pulsation Dampener) "; 506 preference, this application is incorporated into this paper by integral body by reference.
Technical field
The present invention relates generally to the reciprocating machine device, such as compressor.More specifically, the present invention relates to be used for the system and method for damping by the pulsation of reciprocating machine device (such as compressor) generation.
Background technique
This part is intended to the All aspects of in the field that maybe be relevant with All aspects of of the present invention of introducing to the reader, and All aspects of of the present invention will be described below and/or advocated.This discussion is considered to help background information to the reader is provided, so that the better understanding of All aspects of of the present invention.Correspondingly, should it is understandable that these statements will be understood with this angle, rather than be read as to admit it is existing technology.
Reciprocal compressor is positive displacement (positive-displacement) device, and it utilizes motor to drive one or more a plurality of pistons via crankshaft and connecting rod.Each piston in compression cylinder, move back and forth with process fluid (for example, rock gas) be drawn among the chamber, with the compression of the process fluid within the chamber, and process fluid is discharged to the output terminal of expectation from the chamber.Yet because the person's character of reciprocal compressor, they are tending towards producing pulsation to a certain degree.These pulsation can cause the pressure and temperature periodic variation of compression process fluid.
Brief Description Of Drawings
When with reference to the specific descriptions below the advantages, the understanding that will improve of various characteristics of the present invention, aspect and advantage, the identical identical part of symbology in all figure, wherein:
Fig. 1 is the perspective view according to the exemplary reciprocal compressor of one embodiment of the invention;
Fig. 2 is the sectional view of the exemplary reciprocal compressor of Fig. 1, and the inner member of said reciprocal compressor is shown;
Fig. 3 is the fragmentary, perspective view of the exemplary reciprocal compressor of Fig. 1 and Fig. 2;
Fig. 4 A is when at the piston within the compression cylinder during at first stroke position, the side sectional view of the exemplary reciprocal compressor of Fig. 3;
Fig. 4 B is when at the piston within the compression cylinder during at second stroke position, the side sectional view of the exemplary reciprocal compressor of Fig. 3;
Fig. 5 is the side view with reciprocal compressor unit of two reciprocal compressor cylinders, and each reciprocal compressor cylinder combines with inlet pulsation bottle and outlet pulsation bottle;
Fig. 6 is the chart that comes from the outlet pressure pulsation of one process fluid in the outlet pulsation bottle of Fig. 5;
Fig. 7 is the fragmentary, perspective view of reciprocal compressor that is utilized in Fig. 3 of the damping of pulsation device outside the main flow path of flow of process fluid; And
Fig. 8 is the chart of outlet pressure pulsation of process fluid that comes from the compression cylinder outlet of Fig. 7.
The detailed description of specific embodiments
One or more a plurality of specific embodiments of the present invention will be described below.These embodiments that are described only are exemplary of the present invention.In order simple and clear description to be provided for these exemplary, all characteristics of actual mode of execution can not be described in specification.Should be understood that; In the exploitation of any actual mode of execution like this; As in any engineering or design object; Must make the objectives that the specific decision-making of numerous mode of executions reaches the developer, such as following system's related constraint and professional related constraint, said system related constraint can change with the different of mode of execution with professional related constraint.And, should be understood that such development possibly be complicacy and time-consuming, but be can't outargue the normal work to do that is design, makes and produce for having benefited from those of ordinary skill of the present disclosure.
When introducing the element of various embodiments of the present invention, article " a/ one ", " an/ one ", " the/ is said ", " said/ is said " or the like are intended to expression has one or more a plurality of elements.Term " comprises/comprising ", " comprising/including ", " having/having " or the like are intended to contain and expression can have the extra element except that listed element.And the use of " top ", " bottom ", " top ", " following " and the variation of these terms are for convenience's sake, and any special orientation of predetermined member not.
Describe in detail as follows, disclosed embodiment comprises the system and method for the negative effect that is used to reduce pulsating wave, and said pulsating wave is created in reciprocator's (such as reciprocal compressor, reciprocating pump, adjacent intake & exhaust valves or the like).In fact, disclosed embodiment can extend to any other application that can have benefited from damping of pulsation.In certain embodiments, the damping of pulsation device can be mounted outside near pulsation wave source and the main flow path at process fluid, and said process fluid is compressed within reciprocal compressor.More specifically, in certain embodiments, the damping of pulsation device can be the damping of pulsation valve chest, and said damping of pulsation valve chest is configured to encase at least in part the valve assembly of reciprocal compressor.The damping of pulsation valve chest can use damping of pulsation material (such as web material, viscoelastic material (for example, viscoelastic polymer), elastic material or its combination) to fill or lining.Viscoelastic material can be called as the material of the time correlation strain (for example, nonlinear strain) that appears in fact about pressure.
Within the damping of pulsation valve chest, use the damping of pulsation material can cause many practical benefits.For example, the acoustic energy within process fluid can near pulsation source by damping, and through the contingent extra pressure loss of the pipeline and the container of other dampings of pulsation technology.This possibly improve the total power consumption of reciprocal compressor.In addition, the damping of pulsation valve chest not only is absorbed in the pulsation level of the pressure wave in the flow of process fluid, goes back the vibration that damping is caused by sound wave.So, the associated device in the upper reaches of reciprocal compressor and reciprocal compressor and downstream and pipeline can be avoided excessive vibration hazard.In addition, because the compressor valve damping pulsation that the damping of pulsation valve chest directly produces in pulsation, the damping of pulsation valve chest can be usually much smaller than other damping of pulsation technology.Therefore, use the damping of pulsation valve chest, the overall apparatus expense of reciprocal compressor can be reduced significantly.
Turn to accompanying drawing now, a kind of exemplary reciprocal compressor 10 is illustrated in Fig. 1.In the embodiment shown at present, reciprocal compressor 10 comprises a pair of compression cylinder 12 that is coupled to framework 14.Multiple inner member can be set within compression cylinder 12 and the framework 14, with in the compression that enables to be introduced in the fluid among the reciprocal compressor 10 within the compression cylinder 12.For example, in certain embodiments, reciprocal compressor 10 can be utilized to compressed natural gas.Yet in other embodiments, reciprocal compressor 10 can be configured and/or be used to compress other fluids.
Mechanical power source or driver 16, such as internal-combustion engine or motor, can be coupled to reciprocal compressor 10 provides machine power to enable the compression of the fluid within compression cylinder 12 to various inner members.Touch such inner member for convenient, as maybe be desired, can be provided in the opening in the framework 14 and can get into said opening selectively through removable lid 18 in order to diagnose or keep in repair purpose.Further, compression cylinder 12 can also comprise the valve assembly 20 that is used to control through the fluid stream of compression cylinder 12.
Though exemplary reciprocal compressor 10 is shown as the reciprocal compressor of two strokes, other compressor configuration also can adopt and have benefited from present disclosed technology.For instance, in other embodiments, reciprocal compressor 10 can comprise the cylinder stroke of varying number, and is such as four-stroke compressor, screw compressor, like that.Further, it is also contemplated that other variation, except that other, comprise the variation of length of stroke, running speed and size.
Fig. 2 is the sectional view of the exemplary reciprocal compressor 10 of Fig. 1, and the inner member of reciprocal compressor 10 is shown.In the embodiment shown at present; The framework 14 of exemplary reciprocal compressor 10 comprises the intermediate body member or the shell 22 of hollow; Said intermediate body member or shell 22 limit inner space 24 substantially; Various inner members can be housed within the said inner space 24, such as crankshaft 26.In one embodiment, intermediate body member 22 can have crooked substantially or columniform shape.Yet, should be noted that according to disclosed embodiment intermediate body member 22 can have other shapes or configuration.
In the running, driver 16 rotation is supported on the crankshaft 26 within the inner space 24 of framework 14.In one embodiment, crankshaft 26 is coupled to slide block 30 through connecting rod 28 and pin 32.Slide block 30 is set within the slide block guide device 34, said slide block guide device 34 substantially from middle body 22 extend and convenient compression cylinder 12 to the connection of reciprocal compressor 10.In one embodiment, though other configurations can be used, reciprocal compressor 10 comprises two slide block guide devices 34, and said two slide block guide devices 34 vertically extend from the relative side of middle body or shell 22 substantially.Rotatablely moving of crankshaft 26 changed the linear reciprocating motion of the slide block 30 within slide block guide device 34 into through connecting rod 28.
Fig. 3 is the fragmentary, perspective view of the exemplary reciprocal compressor of Fig. 1 and Fig. 2.As directed, reciprocal compressor 10 comprises in the compression cylinder 12 that is coupled to framework 14.As shown in Fig. 3, various parts and lid are removed from reciprocal compressor 10.Yet reciprocal compressor 10 comprises multiple as above with reference to the described similar parts of figure 1 and Fig. 2.For example, framework 14 comprises the intermediate body member 22 with inner space 24, and said intermediate body member 22 contains crankshaft 26.In addition, intermediate body member 22 is coupled to a pair of slide block guide device 34, and said a pair of slide block guide device 34 is guided compression cylinder 12 separately into.
In certain embodiments, process fluid (for example, rock gas) can be as shown in arrow 40, be received among the compression cylinder 12 through compression cylinder inlet 38, and can be as shown in arrow 44, be discharged through compression cylinder outlet 42.As shown in arrow 46; When piston 36 moves around within the inside of compression cylinder 12; Process fluid will get among first and second chambeies within the compression cylinder 12, and wherein process fluid is described in more detail as below, is compressed with the mode that replaces.In addition, a plurality of first order and second level valve assemblys that are present in the first order and the second level valve shell 48,50 can help to be controlled at the flow of process fluid of passing through first and second chambeies within the compression cylinder 12 respectively.
For example, Fig. 4 A and Fig. 4 B illustrate how to flow through first and second chambeies 52,54 of compression cylinder 12 of reciprocal compressor 10 of Fig. 3 of process fluid.Especially, as shown in arrow 58, Fig. 4 A is when one in the slide block that is connected to Fig. 2 30 axle 56 when causing making that piston 36 moves to first stroke position, the side sectional view of compression cylinder 12.In this position, as shown in arrow 60, process fluid can enter the mouth through compression cylinder and 38 be inhaled among first chamber 52.Especially, the first inlet valve assembly 62 can get into first chamber 52 to allow process fluid at open position.Yet the first outlet valve assembly 64 can leave first chamber 52 to stop process fluid through compression cylinder outlet 42 in operating position.
On the contrary, when piston 36 during at first stroke position shown in Fig. 4 A, process fluid will not be inhaled among second chamber 54 of compression cylinder 12.On the contrary, the second inlet valve assembly 66 can get into second chamber 54 to stop process fluid through compression cylinder inlet 38 in operating position.Yet as shown in arrow 70, the second outlet valve assembly 68 can leave second chamber 54 to allow process fluid through compression cylinder outlet 42 at open position.Especially, when piston 36 during at first stroke position, the process fluid in second chamber 54 is compressed, and the process fluid in first chamber 52 is not compressed as yet.
Through mode of comparing, shown in arrow 72, Fig. 4 B is when axle 56 causes piston 36 to move to second stroke position, the side sectional view of compression cylinder 12.In this position, shown in arrow 74, process fluid is inhaled among second chamber 54 through compression cylinder inlet 38.Especially, the second inlet valve assembly 66 can get into second chamber 54 to allow process fluid at open position.Yet the second outlet valve assembly 68 can leave second chamber 54 to stop process fluid through compression cylinder outlet 42 in operating position.
On the contrary, when piston 36 during at second stroke position shown in Fig. 4 B, process fluid will not be inhaled among first chamber 52 of compression cylinder 12.On the contrary, the first inlet valve assembly 62 can get into first chamber 52 to stop process fluid through compression cylinder inlet 38 in operating position.Yet, shown in arrow 76, the first outlet valve assembly 64 can leave first chamber 52 to allow process fluid through compression cylinder outlet 42 at open position.Especially, when piston 36 during at second stroke position, the process fluid in first chamber 52 is compressed, and the process fluid in second chamber 54 is not compressed as yet.
Therefore, when piston 36 between first and second stroke positions shown in Fig. 4 A and Fig. 4 B during translation, process fluid will be to be compressed in first and second chambeies 52,54 of mode within compression cylinder 12 that replace.More specifically, when process fluid with the mode that replaces when being compressed, the first and second inlet valve assemblies 62,66 and the first and second outlet valve assemblies 64,68 can help to control the flow of process fluid through first and second chambeies 52,54.
In certain embodiments, valve assembly can combine with hydrostatic column, and said hydrostatic column can be worked as valve assembly and between the open and close position, played the Protective valve assembly alternately the time.Especially; The first inlet valve assembly 62 can combine with the first inlet valve housing 78; The first outlet valve assembly 64 can combine with the first outlet valve housing 80; The second inlet valve assembly 66 can combine with the second inlet valve housing 82, and the second outlet valve assembly 68 can combine with the second outlet valve housing 84.These valve chests 78,80,82,84 can encase their valve assemblys 62,64,66,68 separately at least in part.
In addition, each in the valve assembly 62,64,66,68 can combine with valve retainer separately, and said valve retainer is they valve assembly fix in position separately.Especially; The first inlet valve assembly 62 can combine with the first inlet valve retainer 86; The first outlet valve assembly 64 can combine with the first outlet valve retainer 88; The second inlet valve assembly 66 can combine with the second inlet valve retainer 90, and the second outlet valve assembly 68 can combine with the second outlet valve retainer 92.
Though shown in Fig. 4 A and Fig. 4 B for only comprising the first and second inlet valve assemblies 62,66 and the first and second outlet valve assemblies 64,68, in certain embodiments, can use numerous combinations of entrance and exit valve assembly.For example, in reciprocal compressor 10, can be used for adapting to higher process fluid flow rate more than two inlet valve assemblies with more than two outlet valve assembly with higher compression process fluid total throughout.Yet; As top described about Fig. 4 A and Fig. 4 B; In certain embodiments, no matter the quantity of inlet in every cover or outlet valve assembly what, reciprocal compressor 10 can be the reciprocal compressor with two strokes of two cover inlets and outlet valve assembly.
With regard to itself character, the reciprocating manner of the compression within reciprocal compressor 10 can be not only in the compression process fluid downstream of reciprocal compressor 10, and produce pulsation to a certain degree at the upper reaches of reciprocal compressor 10.This at least partly is because the mode that replaces; In the said mode that replaces; Two spaces of the process fluid in the compression cylinder 12 of reciprocal compressor 10 (for example, process fluid space in first chamber 52 and another space of process fluid in second chamber 54) be compressed.In other words, the acceleration and the deceleration of the piston 36 in first and second chambeies 52 of compression cylinder 12, between 54 cause the pulsating pressure waves in flow of process fluid.Thereby, pressure wave will be substantially within process fluid in updrift side (for example, backward through compression cylinder inlet 38) and the two propagation of downstream direction (for example, exporting 42 through compression cylinder forward) about reciprocal compressor 10.
This pressure-wave emission can be estimated so that the pressure of compressed process stream body is difficult; Also produce can near and might surpass the pressure of rated pressure of pipeline and other equipment (for example, reciprocal compressor shell 22, crankshaft 26, valve or the like) of contiguous reciprocal compressor 10.In addition, under extreme case, pulsation (surge) situation that rises and falls can cause the excessive level of vibration within reciprocal compressor 10 potentially, and this possibly cause the wearing and tearing of reciprocal compressor 10 and pipeline that is associated and equipment or damage.So, minimize the pulsation influence that is created in the process fluid technology can so that reciprocal compressor 10 can estimate more with reliable.
A kind of method that is used to handle pulsation problem recited above is to use large-scale container, and said large-scale container can be called as the pulsation bottle, and said pulsation bottle is absorbed in kinetic energy and some in the potential energy in the flow of process fluid.Fig. 5 is the side view with reciprocal compressor unit 94 of two reciprocal compressors 10, and each reciprocal compressor 10 combines with inlet pulsation bottle 96 and outlet pulsation bottle 98.More specifically, each in the inlet pulsation bottle 96 can be the upper reaches of the compression cylinder inlet 38 of their reciprocal compressors 10 separately, and in the outlet pulsation bottle 98 each can be the downstream of the compression cylinder outlet 42 of their reciprocal compressors 10 separately.
The two comprises inner separating diaphragm and damp tube substantially entrance and exit pulsation bottle 96,98.Because the area in the bottle 96,98 of pulsing increases, the big space that the separating diaphragm of pulsation bottle 96,98 provides the flow velocity of permission flow of process fluid to be lowered.In addition, the damp tube of pulsation bottle 96,98 provides the decay of pressure wave in flow of process fluid.The kinetic energy of the two absorption technique fluid stream of separating diaphragm and damp tube causes the decline of the maximum fluctuation pressure of flow of process fluid.Especially, flow of process fluid is directly flowed through as the pulsation bottle 96,98 of damping of pulsation device.In other words, the inlet of flow of process fluid through separately gets into pulsation bottle 96,98 and leaves pulsation bottle 96,98 through outlet separately.So, damping of pulsation directly occurs on the main flow path of flow of process fluid.
Yet as shown in fig. 5, pulsation bottle 96,98 and the pipeline and the equipment that are associated can be normally very large-scale, and, therefore make expensive.In addition, because pulsation bottle 96,98 reduces the flow velocity of flow of process fluid effectively, pulsation bottle 96,98 causes sizable pressure loss.So, pulsation bottle 96,98 influences the total efficiency of reciprocal compressor unit 94 unfriendly.Especially, the energy consumption of reciprocal compressor unit 94 directly is lost in the pulsation bottle 96,98 to a certain degree.In addition, some in the also common permission dither of pulsation bottle 96,98 ripple spills.
For example, Fig. 6 is the chart 100 that comes from the outlet pressure pulsation of one process fluid in the outlet pulsation bottle 98 of Fig. 5.As shown, the average outlet pressure 102 of process fluid can be 1500 pounds in an atmosphere (psia) per square inch.As shown, the pulsation between the minimum outlet pressure 108 of the maximum outlet pressure 106 of 1550psia and 1450psia of actual outlet pressure 104.That yes is exemplary and be not intended to restriction for the average outlet pressure 102 of 1500psia.On the contrary; Be intended to substantially set up baseline in the pulsating quantity shown in Fig. 6 for the pulsating quantity that when using in the above, occurs about the described pulsation bottle of Fig. 5 96,98, said baseline can after come to compare with the pulsating quantity of other damping of pulsation embodiments appearance of described use in this article.
Aforesaid, one in the shortcoming of the pulsation bottle 96,98 of use Fig. 5 is the pressure loss amount that when the flow velocity of flow of process fluid reduces, is caused.This at least part be because damping of pulsation directly occurs in the fact on the main flow path of flow of process fluid.In other words; Because damping of pulsation occurs in the entrance and exit pulsation bottle 96,98 of direct Fig. 5 on the main flow path of flow of process fluid; The damping of pulsation level directly occurs on the flow of process fluid (for example, the loss of kinetic energy and the potential energy through flow of process fluid).A kind of method of damping of pulsation of the pulsation bottle 96,98 that is used to improve Fig. 5 can be damping of pulsation to be shifted out the main flow path of flow of process fluid.
Fig. 7 is the fragmentary, perspective view of the reciprocal compressor 10 of Fig. 3, and said reciprocal compressor 10 is utilized in the damping of pulsation device outside the main flow path of flow of process fluid.Especially; Can have one or more a plurality of first inlet valve housing 78, one or more a plurality of first outlet valve housing 80, one or more a plurality of second inlet valve housings 82 at the compression cylinder shown in Fig. 7 12, and one or more a plurality of second outlet valve housings 84.As above described about Fig. 4 A and Fig. 4 B; The first inlet valve housing 78 can encase the first inlet valve assembly 62 at least in part; The first outlet valve housing 80 can encase the first outlet valve assembly 64 at least in part; The second inlet valve housing 82 can encase the second inlet valve assembly 66 at least in part, and the second outlet valve housing 84 can encase the second outlet valve assembly 68 at least in part.
In addition, each in the valve chest 78,80,82,84 can be connected to the valve retainer, and said valve retainer is they valve assembly fix in position separately.Again; As above described about Fig. 4 A and Fig. 4 B; The first inlet valve housing 78 can be connected to the first inlet valve retainer 86; The first outlet valve housing 80 can be connected to the first outlet valve retainer, 88, the second inlet valve housings 82 can be connected to the second inlet valve retainer 90, and the second outlet valve housing 84 can be connected to the second outlet valve retainer 92.
Damping of pulsation device in the embodiment shown in Fig. 7 can be positioned within each in the valve chest 78,80,82,84, rather than uses as above and come damping of pulsation about Fig. 5 and the described pulsation bottle 96,98 of Fig. 6.By this way, damping of pulsation can more be settled near pulsation source (for example, in the above about first and second chambeies 52,54 of Fig. 4 A and the described compression cylinder 12 of Fig. 4 B).So, pulsation can be minimized before they are among the upstream and downstream direction propagates into pipe-line system.
In addition, in valve chest 78,80,82,84, settle damping of pulsation damping of pulsation to be moved on to outside the main flow path of flow of process fluid.In other words, the damping of the dither ripple in flow of process fluid occurs in the inner space that is tangential to the reciprocal compressor 10 that process fluid flows through.More specifically, flow of process fluid is not flowed through as the valve chest 78,80,82,84 of damping of pulsation device.In fact, in certain embodiments, be described below, Sealing can be used for fully that flow of process fluid is isolated with the inner space of the valve chest 78,80,82,84 that can comprise the damping of pulsation material.So, the damping of pulsation of flow of process fluid takes place outside main flow path.In other words, damping of pulsation does not directly occur in the main flow path of flow of process fluid.
In certain embodiments; The damping of pulsation of valve chest 78,80,82,84 can be through accomplishing to the inner space of valve chest 78,80,82,84 with suitable damping material filling or lining; Absorbing the pressure wave energy harmony wave energy directly come from flow of process fluid, and appreciable pressure loss and/or kinetic energy and potential energy loss are not incorporated among the flow of process fluid.In certain embodiments; The inner space of valve chest 78,80,82,84 can (for example fully filled with the damping of pulsation material; 100%) or partly fills (for example, 10%, 20%, 30%, 40%, 50%, 60%, 70%, 80%, 90% or the like).In other embodiments, the inner space of valve chest 78,80,82,84 can have the damping of pulsation material of lining inner space inwall.
In certain embodiments; Use valve chest 78,80,82, damping material within 84 can be the silk screen of various density, various damping capacities viscoelastic material (for example; Viscoelastic polymer or foam), a kind of in all kinds of elastic material, perhaps their combination.Always, the damping material of use can be any material with pressure and acoustics damping characteristic.More specifically, the type of the energy of these material absorption is acoustic energy, vibrational energy and pressure pulsation, and said material can be heat energy or friction energy with the transformation of energy of these types.So, any transformation of energy that can absorb friction energy or coulomb energy inherently and will absorb can be suitable for as the damping of pulsation material for the material of heat.
Use the damping of pulsation material can cause many practical benefits at the valve chest 78,80,82 of the valve assembly that encases compression cylinder 12 62,64,66,68, within 84.For example, the acoustic energy within process fluid can approach pulsation source by damping, and the extra pressure loss that the container (for example, the pulsation bottle 96,98 of Fig. 5 and Fig. 6) that does not have possibility to pass through pipeline and other damping of pulsation technology takes place.
For example, Fig. 8 is the chart 110 of outlet pressure pulsation of process fluid that comes from the compression cylinder outlet 42 of Fig. 7.As shown, the average outlet pressure 102 of process fluid also can be 1500psia.Yet; As shown; Before being compared to (for example; Pulsation between the minimum outlet pressure 108 of the maximum outlet pressure 106 of 1550psia and 1450psia Fig. 5), actual outlet pressure 104 be pulsation between the minimum outlet pressure 108 of the maximum outlet pressure 106 of 1510psia and 1490psia only.In other words; Be compared to the pulsation bottle 96,98 that uses Fig. 5, the valve chest 78,80,82 of the valve assembly 62,64,66,68 of the compression cylinder that encases Fig. 7 12, use within 84 the damping of pulsation material can be at minimum and maximum outlet pressure 106, cause littler in fact variation between 108.
In addition, use the damping of pulsation material not only to be absorbed in the pulsation level of the pressure wave in the flow of process fluid at the valve chest 78,80,82 of the valve assembly that encases compression cylinder 12 62,64,66,68, within 84, the also vibration that causes by sound wave of damping.So, excessive vibration hazard can be avoided in the pipeline upper reaches of reciprocal compressor 10 and associated device and reciprocal compressor 10 and downstream.In addition, the extra pressure loss that is caused by the pulsation bottle 96,98 of Fig. 5 can be reduced owing to the damping of pulsation that outside the main flow path of flow of process fluid, takes place significantly.This will reduce the total power consumption of reciprocal compressor 10.In addition, valve chest 78,80,82,84 common pulsation bottles 96,98 much smaller than Fig. 5.For example, in certain embodiments, valve chest 78,80,82,84 can be little more about 5%, 10%, 15%, 20%, 25%, 30%, 35%, 40%, 45%, 50% than the pulsation bottle of Fig. 5 96,98, perhaps more.Therefore, use the damping of pulsation material at the valve chest that encases valve assembly 62,64,66,68 78,80,82, within 84, the overall apparatus expense of reciprocal compressor 10 can be reduced significantly.
Although the present invention possibly have various modifications and alternative, specific embodiments is illustrated with embodiment's mode in the accompanying drawings, and is specifically described in this article.Yet, should be appreciated that the present invention is not intended to be limited to the particular form that is disclosed.On the contrary, the present invention drops on all modifications, equivalent and substitute in the spirit and scope of the present invention that following appending claims limits with covering.
Claims (20)
1. system, said system comprises:
Compressor; Said compressor has first chamber, inlet, outlet, the first inlet valve assembly and the first outlet valve assembly; The said first inlet valve assembly is configured to control the flow of process fluid that gets into said first chamber of said compressor through said inlet; The said first outlet valve assembly is configured to control the said flow of process fluid of leaving said first chamber of said compressor through said outlet, and wherein said flow of process fluid limits flow path; And
At least one damping of pulsation device, said at least one damping of pulsation device is outside said flow path, and wherein said damping of pulsation device is configured to the pulsating wave of damping in said process fluid.
2. the said system of claim 1, wherein said at least one damping of pulsation device comprises the damping of pulsation valve chest, wherein said damping of pulsation valve chest encases at least a portion of said first inlet valve assembly or the said first outlet valve assembly.
3. the said system of claim 2, wherein fill with the damping of pulsation material inner space of each damping of pulsation valve chest.
4. the said system of claim 3, wherein said damping of pulsation material comprises web material.
5. the said system of claim 3, wherein said damping of pulsation material comprises viscoelastic material.
6. the said system of claim 3, wherein said damping of pulsation material comprises elastic material.
7. the said system of claim 2, wherein said compressor comprises reciprocal compressor.
8. the said system of claim 7, wherein said reciprocal compressor comprises the reciprocal compressor of two strokes.
9. the said system of claim 8; The reciprocal compressor of wherein said two strokes comprises second chamber, the second inlet valve assembly and the second outlet valve assembly; The said second inlet valve assembly is configured to control the flow of process fluid in said second chamber that gets into the reciprocal compressor of said two strokes through said inlet, and the said second outlet valve assembly is configured to control the said flow of process fluid in said second chamber of leaving the reciprocal compressor of said two strokes through said outlet.
10. the said system of claim 9, each is encased the wherein said first inlet valve assembly, the said first outlet valve assembly, the said second inlet valve assembly and the said second outlet valve assembly within damping of pulsation valve chest separately at least in part.
11. a system, said system comprises:
Damping of pulsation device, said damping of pulsation device are configured to outside the flow path of compressed process fluid within the reciprocal compressor, to be coupled to said reciprocal compressor.
12. the said system of claim 11, wherein said damping of pulsation device comprises the damping of pulsation valve chest, and said damping of pulsation valve chest is configured to encase at least in part the valve assembly of said reciprocal compressor.
13. the said system of claim 12, fill with the damping of pulsation material at least in part the inner space of wherein said damping of pulsation valve chest.
14. the said system of claim 13, wherein said damping of pulsation material comprises web material.
15. the said system of claim 13, wherein said damping of pulsation material comprises viscoelastic material.
16. the said system of claim 13, wherein said damping of pulsation material comprises elastic material.
17. the said system of claim 11 comprises said reciprocal compressor, wherein said damping of pulsation device is coupled to said reciprocal compressor.
18. a method, said method comprises:
Use the damping of damping of pulsation device by the pulsating wave in process fluid that reciprocator produces, be installed in said damping of pulsation device in the said reciprocator outside the flow path of the said process fluid of the said reciprocator that flows through.
19. the said method of claim 18, wherein the step of the said pulsating wave of damping in said process fluid comprises the said pulsating wave of use damping of pulsation valve chest damping, and said damping of pulsation valve chest encases the valve assembly of said reciprocator at least in part.
20. the said method of claim 19, wherein the step of the said pulsating wave of damping in said process fluid comprises the said pulsating wave of use damping of pulsation material damping, and said damping of pulsation material is within the inner space of said damping of pulsation valve chest.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US12/620,506 US20110116940A1 (en) | 2009-11-17 | 2009-11-17 | Viscoelastic compressor pulsation dampener |
| US12/620,506 | 2009-11-17 | ||
| PCT/US2010/052198 WO2011062705A1 (en) | 2009-11-17 | 2010-10-11 | Viscoelastic compressor pulsation dampener |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102667152A true CN102667152A (en) | 2012-09-12 |
Family
ID=44011406
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010800521244A Pending CN102667152A (en) | 2009-11-17 | 2010-10-11 | Viscoelastic compressor pulsation dampener |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20110116940A1 (en) |
| CN (1) | CN102667152A (en) |
| BR (1) | BR112012011690A2 (en) |
| GB (1) | GB2488087A (en) |
| RU (1) | RU2554661C2 (en) |
| WO (1) | WO2011062705A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109869299A (en) * | 2017-12-05 | 2019-06-11 | 翰昂汽车零部件有限公司 | The accurate control of sucking damping unit in compressor with variable displacement |
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| US20140271250A1 (en) * | 2013-03-15 | 2014-09-18 | Cameron International Corporation | Compression System and Method Having Co-Axial Flow Device |
| DE102015110883A1 (en) * | 2015-07-06 | 2017-01-12 | J. Wagner Gmbh | Pulsationsdämpfungssystem |
| US11085427B2 (en) * | 2018-03-25 | 2021-08-10 | Justin P. Manley | Pulsation dampener utilizing a chargless mitigation device |
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| CN109869299B (en) * | 2017-12-05 | 2020-12-04 | 翰昂汽车零部件有限公司 | Precise control of suction damping device in variable displacement compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| RU2554661C2 (en) | 2015-06-27 |
| GB201210610D0 (en) | 2012-08-01 |
| WO2011062705A1 (en) | 2011-05-26 |
| GB2488087A (en) | 2012-08-15 |
| RU2012124791A (en) | 2013-12-27 |
| BR112012011690A2 (en) | 2019-05-28 |
| US20110116940A1 (en) | 2011-05-19 |
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