US20040234386A1 - Discharge muffler having an internal pressure relief valve - Google Patents
Discharge muffler having an internal pressure relief valve Download PDFInfo
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- US20040234386A1 US20040234386A1 US10/440,763 US44076303A US2004234386A1 US 20040234386 A1 US20040234386 A1 US 20040234386A1 US 44076303 A US44076303 A US 44076303A US 2004234386 A1 US2004234386 A1 US 2004234386A1
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- tube
- discharge
- muffler
- housing
- chamber
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- 239000003507 refrigerant Substances 0.000 claims abstract description 65
- 239000012530 fluid Substances 0.000 claims abstract description 51
- 238000004891 communication Methods 0.000 claims abstract description 15
- 238000007599 discharging Methods 0.000 claims abstract description 3
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- 230000008569 process Effects 0.000 description 2
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- 230000004913 activation Effects 0.000 description 1
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- 238000009826 distribution Methods 0.000 description 1
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Images
Classifications
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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
- F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
- F04B39/0061—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes using muffler volumes
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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
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/123—Fluid connections
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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
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/02—Stopping, starting, unloading or idling control
- F04B49/03—Stopping, starting, unloading or idling control by means of valves
-
- 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
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/10—Other safety measures
Abstract
A muffler for use in a refrigerant compressor which includes a muffler housing, an intake tube at one end of the muffler housing for receiving a flow of refrigerant fluid, and an exhaust tube at another end opposed of the muffler housing to exhaust the flow of refrigerant fluid. The muffler housing is adapted to structurally carry a pressure relief member therein. The pressure relief member is in fluid communication with the intake tube. A discharge tube is connected to the exhaust tube for transporting the flow of refrigerant fluid from the exhaust tube to a compressor discharge port for discharging the refrigerant fluid from the compressor.
Description
- This Application is related to Application No. ______, filed contemporaneously with this Application on May 19, 2003, entitled “MUFFLER SYSTEM FOR A COMPRESSOR” assigned to the assignee of the present invention and is incorporated herein by reference.
- The present invention is directed to an internal muffler for use with a compressor, and more specifically to a muffler for use on the high-pressure discharge side of a compressor used in refrigeration and heating and cooling systems.
- Compressors are one of several components in cooling and heating systems. The compressor is typically used in combination with a condenser, expansion valves, an evaporator and blowers to heat or cool a space.
- The compressor itself typically is a hermetically sealed device that has an intake port and a discharge port. The hermetically sealed device typically is a metallic shell that houses an electric motor and a mechanical apparatus for compressing gas. For most compressor designs, the gas cavity enclosed by the housing serves as a reservoir of low-pressure gas to be drawn into the mechanical section of the compressor. The electric motor is connected to a power source that provides line power for operation. The motor in turn drives the mechanical apparatus for compressing gas. Compressors are typically categorized by the mechanical apparatus that compresses the gas. For example, compressors using a piston device to compress the refrigerant gas are referred to as reciprocating compressors. While there are differences among the compressors as to how refrigerant gas is compressed, the basic principles of operation are common among the compressors, i.e., gas is drawn in through the gas intake during operation, the gas is compressed in the mechanical apparatus of the compressor and the highly compressed gas is discharged through an outlet port.
- Various mufflers have been employed to eliminate, reduce or otherwise attenuate compressor noise. Typically, mufflers are positioned on the discharge or high pressure side of the compressor, such as at the cylinder head of a piston-driven compressor, and increase the length of flow of the gas by having it travel a tortuous path through openings of varying size or additionally define an elongate “expansion” chamber to effect sound wave stability. Placement of an expansion chamber adjacent the discharge side not only reduces operating efficiency of the compressor, but increases the overall size of the compressor. The muffler is then connected to a shockloop, also referred to as a discharge tube, that extends to a discharge port in the compressor housing that connects to a condenser that is outside the compressor housing via a conduit. Collectively, the shockloop or discharge tube is often referred as a “shockloop cane” which describes its shape. However, to regulate the discharge gas pressure level, an internal pressure relief valve (IPRV) is placed in fluid communication along the discharge path. The IPRV typically employs (within a cylindrical valve body) a spring that is maintained in a compressed condition against a plunger. The plunger overcomes the directed spring force and actuates toward an open position in the valve body of the IPRV in response to excessive discharge gas pressure levels until sufficient discharge gas is bled through the IPRV, wherein the plunger returns to its closed position within the valve body. The IPRV may be positioned downstream of the muffler, such as along the discharge tube. This is accomplished by splicing the IPRV into the discharge tube which requires the discharge tube to be severed into two separate pieces, inserting a component, such as an adapter for securing the IPRV between the severed ends of the discharge tube, then reattaching the severed ends to opposite ends of the component, which reattachment is usually accomplished by brazing. Such operations increase the number of compressor parts, the time required to assemble the compressor, and likewise, the cost to fabricate the compressor. Further, any combination of severing the discharge tube and then reattaching the severed ends of the discharge tube to opposed ends of an inserted component to achieve a contiguous discharge tube construction, especially when the method of reattachment is a heat-intensive process, will invariably impose prestresses in the discharge tube. The magnitude of these prestresses may be significantly increased if the inserted component and the discharge tube are constructed of different materials having different coefficients of expansion/contraction.
- In addition to the slicing operation, the discharge tube must be subsequently manipulated to connect its ends to the respective parts inside the compressor housing. Alignment of the ends of the discharge tube with the respective mating parts is critical to minimize the introduction of additional prestresses in the discharge tube. Typically, an end of the discharge tube is connected to the muffler via a port formed in a sidewall of the muffler housing. The muffler is typically vertically oriented within the compressor housing by threaded engagement with the cylinder head so that alignment between the muffler port and the discharge tube occurs only at a specific angular position of the muffler port about the axis of the threaded engagement. Even a slight deviation from the aligned position may introduce additional prestresses in the discharge tube possibly adversely affecting the useful life of the compressor.
- What is needed is a compact, discharge-side muffler design for maintaining compressor operating efficiency while simultaneously reducing the number of compressor parts and improving the magnitude of prestresses to which the discharge tube is subjected.
- The present invention relates to a discharge muffler system for use in a refrigerant compressor, including a tube inside a refrigerant compressor having a first end for receiving a flow of pressurized refrigerant fluid and a second end for exhausting the flow of pressurized refrigerant fluid. A housing surrounds the tube between the first end and the second end, the housing and the tube defining a chamber therebetween, the chamber being in fluid communication with the refrigerant fluid flowing in the tube. A pressure relief member is connected to the housing and is configured and disposed to regulate fluid pressure in the chamber. The pressure relief member regulates pressure in the chamber by actuating to an open position in response to a pressure in the chamber exceeding a predetermined pressure level to vent a portion of the refrigerant fluid in the chamber to an exterior of the housing. A unitary discharge tube receives the flow of pressurized refrigerant fluid from the second end and exhausts the flow of the pressurized refrigerant fluid from the refrigerant compressor.
- The present invention also relates to a method for assembling a discharge muffler and discharge tube for use in a refrigerant compressor, the steps include: providing a discharge muffler having a muffler housing; providing an intake tube at a first end of the muffler housing for receiving a flow of refrigerant fluid, the intake tube being configured for connection with a cylinder head of a refrigerant compressor; providing an exhaust tube at a second end of the muffler housing opposite the first end to exhaust the flow of refrigerant fluid from the discharge muffler, the exhaust tube being configured for connection with a discharge tube, and the intake tube, the exhaust tube and the connection with the cylinder head being substantially coaxial; providing a discharge tube having an intake for connection to the exhaust tube and having an exhaust for connection to a discharge port of the refrigerant compressor, the discharge tube transporting the flow of refrigerant fluid from the exhaust tube to the compressor discharge port for discharging the refrigerant fluid from the compressor; providing a driving tool for connecting the discharge muffler to the cylinder head; the driving tool having an aperture; directing the aperture of the driving tool over the exhaust tube until the driving tool and the discharge muffler are sufficiently engaged wherein the discharge muffler is actuated in response to an actuating force being applied to the driving tool; directing the intake tube of the discharge muffler in engagement with the driving tool into mutual alignment with the cylinder head; applying the actuating force to the driving tool until the discharge muffler is connected to the cylinder head; connecting the exhaust tube to the intake of the discharge tube; and connecting the exhaust of the discharge tube to the discharge port.
- An advantage of the present invention is the inclusion of a compact compressor muffler for permitting reduction in the overall size of the compressor while maintaining compressor efficiency.
- Another advantage of the present invention is that the muffler of the present invention is adapted to accept an IPRV therein, thereby reducing part count, labor costs and the likelihood of introducing prestresses in the discharge tube.
- Another advantage of the present invention is that the assembly of the discharge tube to connect the muffler to the exhaust port in the compressor housing is greatly simplified.
- Another advantage of the present invention is that the IPRV will not actuate as often within the compressor by virtue of pressure damping.
- Other features and advantages of the present invention will be apparent from the following more detailed description of the preferred embodiment, taken in conjunction with the accompanying drawings which illustrate, by way of example, the principles of the invention.
- FIG. 1 is a cross-section of a refrigerant compressor that incorporates a muffler system of the present invention;
- FIG. 2 is a partial elevation view of the discharge tube of the present invention taken along line11-11 of FIG. 1;
- FIG. 3 is a perspective view of a muffler of the present invention;
- FIG. 4 is a cross-section of the muffler being joined to the discharge tube of the present invention;
- FIG. 5 is a perspective view of a tool for the installing the muffler of the present invention;
- FIG. 6 is an enlarged cross section of an alternate embodiment of the muffler being joined to the discharge tube of the present invention; and
- FIG. 7 is an elevation view of a discharge tube of the present invention.
- Wherever possible, the same reference numbers will be used throughout the drawings to refer to the same or like parts.
- One embodiment of a compressor that incorporates the discharge muffler and discharge tube or shockloop of the present invention is depicted in FIG. 1. The
compressor 2 is connected to a conventional refrigeration or heating, ventilation and air conditioning (HVAC) system (not shown), such as may be found in a refrigerator, home or automobile, having a condenser, expansion device and evaporator in fluid communication.Compressor 2 is preferably a reciprocating compressor connected to an evaporator (not shown) by a suction line that enters thesuction port 14 ofcompressor 2.Suction port 14 is in fluid communication withsuction plenum 12. Refrigerant gas from the evaporator enters the low pressure side ofcompressor 2 throughsuction port 14 and then flows to thesuction plenum 12 before being compressed. -
Compressor 2 includes anelectrical motor 18. A standard induction motor having astator 20 and a rotor 22 is shown. However any other suitable type of electrical motor may be used. Ashaft assembly 24 extends through rotor 22. Thebottom end 26 ofshaft assembly 24 opposite themotor 18 extends into a lubrication sump 28 and includes a series ofapertures 27. Connected toshaft assembly 24 below the motor is at least one piston assembly 29. Thecompressor 2 illustrated in FIG. 1 has acylinder head 30 having two piston assemblies 29. A connectingrod 32 is connected to thepiston head 34 which moves back and forth withincylinder 36.Cylinder head 30 includes agas inlet port 38 and agas discharge port 40. Theseports Gas inlet port 38 is connected to anintake tube 54 which is connected to thesuction plenum 12 enclosed withincompressor housing 16. - Upon activation of
motor 18,shaft assembly 24 begins to turn or rotate. Rotation ofshaft assembly 24 causes reciprocating motion of the piston assemblies. As one piston assembly moves to an intake position, i.e., aspiston head 34 moves away fromgas discharge port 40, a suction valve opens and refrigerant gas or vapor is introduced into an expandingcylinder 36 volume. This gas is pulled from withinsuction plenum 12 throughintake tube 54 togas inlet port 38 where it passes through the suction valve(s) and is introduced intocylinder 36. When a piston assembly reaches a first end (or top) of its stroke, shown by movement ofpiston head 34 to the right side ofcylinder 36 in FIG. 1, suction valve(s) close. Thepiston head 34 then compresses the refrigerant gas by reducing thecylinder 36 volume. When piston assembly 29 moves to a second end (or bottom) of its stroke, shown by movement ofpiston head 34 to the left side ofcylinder 36 in FIG. 1, discharge valve(s) are opened and the highly compressed refrigerant gas is expelled throughgas discharge port 40 into amuffler 50 then through a discharge tube orshockloop 52, exiting thecompressor housing 16 via an exhaust or dischargeport 15. Asecond muffler 56 can be connected between the exhaust or dischargeport 15 outlet and the condenser. This comprises one cycle of the piston assembly which is continuously repeated during operation of the compressor. - The cyclic opening and closing of the suction valve(s) along with the periodic starting and stopping of the flow of refrigerant gas generates a high level of noise over a broad frequency range. The placement of
muffler 56 physically outsidecompressor housing 16 along theconduit connecting compressor 2 and the condenser assists in absorbing the broadband sound generated by the cyclic motion of the suction valve(s) and the cyclic surging of the gas. Further, locatingmuffler 56outside compressor housing 16, not only permits a reduction in size of thecompressor housing 16, but enhances the effectiveness ofmuffler 56 without adversely affecting the efficiency of thecompressor 2. Furthermore,muffler 50 additionally regulates the cyclic gas surges by employing anIPRV 60, or any other suitable pressure relief member or valve. - Referring to FIGS. 2-5,
muffler 50 helps regulate cyclic gas surges by employing theIPRV 60 therein as previously discussed.Muffler 50 preferably includes atube 62 having opposed ends 76, 78. A threadedmember 64 having alip 80 at one end is positioned overend 78 oftube 62 for threadedly engaging thecylinder head 30 to maintaintube 62 in fluid communication withgas discharge port 40. Preferably, theend 78 oftube 62 and the end of threadedmember 64 oppositelip 80 are substantially coincident to ensure the parts are sufficiently engaged therebetween. Alternately, threadedportion 64 may be integrally formed withtube 62 ortube 62 may have external threads formed along its length, whereinhousing opening 72 would be similarly sized with that of housing opening 70 so that the external threads oftube 62 would just slide inside thehousing openings 70, 72 for ease of securing thehousing openings 70, 72 ofhousing 68 to thetube 62. Ahousing 68 includes opposedopenings 70, 72 which permits opening 70 ofhousing 68 to be positioned overend 78 oftube 62 and moved alongtube 62 until opening 72 ofhousing 68 is in a position to sufficiently contactlip 80 when assembled. Preferably,housing 68 is coaxial withtube 62 alongaxis 84. Alternatively,housing 68 and threadedportion 64 may be of unitary construction. Methods of securingtube 62,housing 68 and threadedportion 64 into their respective positions can include spot welding, soldering, brazing, or by press-fit.Housing 68 is substantially cylindrical in profile and defines anannular chamber 82 betweentube 62 andhousing 68.Tube 62 andhousing 68 are preferably maintained in fluid communication by a pair ofapertures 66 formed intube 62. However, any number ofapertures 66 can be used to maintain this fluid connection. - An additional aspect of the
apertures 66 is to regulate the amount of lubricant oil, also referred to as lubricant liquid, that may collect within thehousing 68 of themuffler 50 during operation of the compressor. If the amount oflubricant oil 67 within thehousing 68 is not regulated below a certain maximum level, the lubricant oil may adversely affect the noise attenuation capability of themuffler 50, possibly including shifting the attenuating frequency to whichmuffler 50 is tuned. Since the muffler is oriented substantially vertical within thecompressor housing 68, thelower aperture 66 is vertically positioned alongtube 62 to maintain thelubricant oil 67 at an acceptable level within thehousing 68. When the level of thelubricant oil 67 in thehousing 68 rises sufficiently above the lower portion ofaperture 66, thelubricant oil 67 simply drains through thelower aperture 66 downtube 62, returning to thecylinder head 30. -
Chamber 82 ofmuffler 50 displaces significantly less volume than mufflers which employ an expansion chamber. Although not necessarily drawn to scale in FIG. 4,chamber 82 displaces a comparable volume as compared totube 62. By virtue of this lack of pronounced volumetric increase ofchamber 82 that is adjacent thedischarge port 40, compressor efficiency is maintained. Additionally, the small size ofhousing 68 permits reduction in size of thecompressor housing 16. -
Muffler 50 further provides for the integral mounting ofIPRV 60 therein. A boss 74 preferably is formed inhousing 68, which extends outwardly or inwardly fromhousing 68 such as by extrusion or other suitable techniques, permittingIPRV 60 to be secured therein by any usual method known in the art such as press fit, threading, adhesive or metal-joining processes involving elevated temperatures. Preferably, boss 74 extends radially outward fromaxis 84 which defines a side branch mounting forIPRV 60 that saves further space within thecompressor housing 16. Alternately, an aperture may be formed inhousing 68 without boss 74 that is sized to receive theIPRV 60. In addition to the space savings made possible by the integral muffler/IPRV construction, due to the pair ofapertures 66 formed intube 62 being in fluid communication withchamber 82 ofhousing 68, the pressure pulses from thedischarge port 40 are dampened, thus significantly reducing the number ofIPRV 60 “actuations” to resolve such over-pressure conditions. Among the over-pressureconditions causing IPRV 60 actuations are compressor start-ups and changes in compressor operating conditions. The noise generated by theIPRV 60 is generally considered undesirable. - Due to the compact construction of
housing 68, for a given material thickness,housing 68 has enhanced stiffness and strength as compared to a conventional muffler having an expansion chamber. This enhanced stiffness not only helps support theIPRV 60, but also permitsmuffler 50 to be collectively threadedly installed onto thecylinder head 30 by a slotted driving tool 86 (see FIG. 5) having anaperture 90 of sufficient size and depth to collectively slide overtube 62 andhousing 68 ofmuffler 50. Drivingtool 86 further has at least oneslot 92 formed along itsperipheral edge 93 that is adapted or configured to engage the boss 74 protruding fromhousing 68. In other words, to utilize drivingtool 86, the drivingtool 86 and themuffler 50 are brought into mutual axial alignment withaxis 84.Peripheral edge 93 of drivingtool 86 is then directed alongaxis 84 indirection 97 so thatperipheral edge 93 first slides overend 76 oftube 62 ofmuffler 50. Drivingtool 86 is then continually directed incrementally indirection 97 to slide overmuffler 50 untilslot 92 of drivingtool 86 sufficiently engages boss 74 ofhousing 68 ofmuffler 50. Once the drivingtool 86 is engaged withmuffler 50, end 78 of threadedportion 64 ofmuffler 50 is then further axially aligned alongaxis 84 and brought into threaded engagement with the corresponding threaded discharge aperture in thecylinder head 30. By then applying a rotational force 88 aboutaxis 84 to drivingtool 86,slot 92 imparts a rotational force along a portion of boss 74 thereby urgingmuffler 50 into rotational movement aboutaxis 84 until threadedportion 64 is sufficiently threadedly engaged with thecylinder head 30. If there is sufficient clearance,IPRV 60 may be mounted inhousing 68 ofmuffler 50 prior to installingmuffler 50 in thecylinder head 30. - By directly mounting the
IPRV 60 in thehousing 68 ofmuffler 50, the compressor part count is reduced, and parts handling is reduced as to thedischarge tube 52, which reduces prestresses indischarge tube 52. Alternately, ifhousing 68 ofmuffler 50 is constructed without the boss 74, such as the aperture previously discussed, and there is insufficient clearance to install theIPRV 60 prior to installing themuffler 50, the drivingtool 86 could simply be modified to employ an inwardly directed member (not shown) to engage the aperture, but would otherwise operate the same as previously discussed. Additionally, by virtue of the connection ofmuffler 50 anddischarge tube 52 being substantially coincident alongaxis 84, or coaxial, alignment between themuffler 50 and end 98 of thedischarge tube 52 is maintained irrespective a deviation from a reference position aboutaxis 84. In other words, unlike a side-mounted prior art muffler port for receiving the discharge tube, which only aligns with the discharge tube at a specific rotation position or orientation about its axis of rotation, themuffler 50 and end 98 ofdischarge tube 52 of the present invention are always in alignment. Therefore, installation of the discharge tube is greatly eased, since the installer must only be concerned with a proper installation torque to install themuffler 50 in the cylinder head, not the possibility of applying insufficient or excessive installation torque to the muffler in an attempt to achieve the specific alignment orientation required between the muffler and the discharge tube. - One end of
discharge tube 52 is connected tomuffler 50. The other end ofdischarge tube 52 is connected to thedischarge outlet 15 ofcompressor 2. A portion of thedischarge tube 52adjacent muffler 50 preferably has a cane or inverted “J” shape, but can have any suitable shape. Referring to FIG. 7, thedischarge tube 52 is preferably of continuous, integral construction extending between the muffler and thedischarge outlet 15. The shape ofdischarge tube 52 is primarily driven by the location and attitude of the two interface locations within thecompressor housing 16 while maintaining sufficient spacing from compressor components. Thus, the path of theunitary discharge tube 52 typically follows a path adjacent thecompressor housing 16, preferably including from end 98 a substantiallystraight portion 116 which extends into a substantiallycurved portion 118 and which similarly extends into a remainingportion 120 that terminates atend 106. Referring back to FIGS. 1, 4 and 6, bothtube 62 ofmuffler 50 and a portion ofdischarge tube 52 share acoincident axis 84. The segment or portion ofdischarge tube 52 that extends alongaxis 84 is of an extended length which more evenly distributes prestresses along the collective axial length oftube 52. Additionally, the joint formed betweendischarge tube 52 andtube 62 ofmuffler 50 is also coincident withaxis 84. In one embodiment,tube 62 ofmuffler 50 has an enlarged diameter portion 94 that extends into a shoulder 96 formed therein that is coincident withaxis 84. - To establish the joint between
tube 62 ofmuffler 50 anddischarge tube 52, anend 98 ofexhaust tube 52 is directed inside the enlarged diameter portion 94 oftube 62past end 76 to the extent required to form the joint, up to “bottoming out” at the shoulder 96. In an alternate embodiment, referring to FIG. 6,tube 62 may be configured to slide insidedischarge tube 52. That is, end 76 oftube 62 is of substantially constant diameter.End 98 ofdischarge tube 52 has anenlarged diameter portion 108 which extends into a shoulder 110. After aligningend 98 ofdischarge tube 52 and end 76 oftube 62 withaxis 84, end 76 oftube 62 is incrementally directed insideenlarged diameter position 108 until “bottoming out” on shoulder 110 ofdischarge tube 52. -
Discharge tube 52 connects in a similar way to dischargeoutlet 15.Discharge outlet 15 includes a fitting 100 that extends through anaperture 112 in thecompressor housing 16. The fitting 100 is provided with a secure joint between itself and thecompressor housing 16 that is both fluid tight and rigid, both to prevent the leakage of refrigerant throughaperture 112 and avoid unnecessary flexure to the subsequent joints formed between both the fitting 100 and thedischarge tube 52 inside thecompressor housing 16 and between the conduit and the fitting 100 located outside thecompressor housing 16. A fitting portion 114 of fitting 100 extends inside thecompressor housing 16 which axially aligns along axis 99 withend 106 oftube 52. Fitting portion 114 that is insidecompressor housing 16 includes anend 102 having anenlarged diameter portion 104. - To establish a joint between the
discharge tube 52 and fitting portion 114, theend 106 ofdischarge tube 52 is directedpast end 102 of fitting portion 114 along axis 99 into theenlarged diameter portion 104 until a joint is formed. The joint may be secured by soldering or other appropriate bonding method. Preferably, the joints for eachend discharge tube 52 is established prior to securing the joints. That is, end 98 ofdischarge tube 52 is directed into enlarged diameter portion 94 and end 106 ofdischarge tube 52 is directed intoenlarged diameter portion 104 of fitting portion 114. Although the order of establishing each joint is not critical, by permitting ends 98, 106 ofdischarge tube 52 tube to slide along the respectivemutual axes 84, 99 with respect to the respectiveenlarged diameter portions 94, 104 after each joint is created, at least a portion of the prestresses normally inherent with the installation of thedischarge tube 52 may be avoided. In other words, by virtue of this variable, coincident insertion distance along enlarged diameter portion 94 betweendischarge tube 52 andtube 62 ofmuffler 50 and betweendischarge tube 52 and fitting portion 114, prestresses in thedischarge tube 52 caused by non-alignment installation conditions may be further reduced, thereby improving the structural integrity of the compressor. Further, by providing a substantially straight orlinear portion 116 indischarge tube 52adjacent end 98, establishing the joint betweenend 98 ofdischarge tube 52 is made easier for the installer and may also reduce the magnitude of prestresses in thedischarge tube 52 by permitting the improved distribution of forces due to the collective extended lengths ofportions discharge tube 52 along ends 98, 106, and between respectiveenlarged diameter portions 94, 104, an amount of lateral movement of ends 98, 106 within the respectiveenlarged diameter portions 94, 104 may occur which would act to further reduce prestresses indischarge tube 52. - In an alternate embodiment, end106 of
discharge tube 52 extends throughaperture 112 of discharge outlet 15 a sufficient length for connection with fitting 114. Preferably, a single brazed joint placed alongaperture 112 collectively provides a secure, fluid tight seal between thehousing 16, thedischarge tube 52 and fitting 114 while subjecting thedischarge tube 52 to minimal prestresses. In this embodiment, end 98 oftube 52 is provided with an amount of both vertical and horizontal adjustment betweenend 98 oftube 52 and enlarged diameter portion 94 ofmuffler 50 as previously discussed.End 106 ofdischarge tube 52 must only extend throughaperture 112 ofhousing 16 and is not otherwise constrained, instead of being constrained to extend along the axis of another component. Further, it is possible to installdischarge tube 52 after all of the other compressor components have been installed in the lower half of the compressor housing. This advantageous combination of slidable connections at each end ofdischarge tube 52 subjects dischargetube 52 to few if any installation prestresses. -
Discharge tube 52 further provides several additional benefits regarding both improved sound attenuation and reduction of liquefied refrigerant that may collect in the sump of thecompressor housing 16. Referring back to FIG. 1, remainingportion 120 ofdischarge tube 52 extends adjacent the bottom ofcompressor housing 16 before exiting atdischarge port 15. Preferably a segment of remainingportion 120 extends substantially coplanar withdischarge port 15. Since the level oflubricant 39 at the lubrication sump 28 is preferably maintained above or at least in contact with remainingportion 120, remainingportion 120 which receives heated discharge refrigerant fluid from thecylinder head 30 is maintained in thermal communication withlubricant 39. By virtue of this thermal communication with remainingportion 120, which becomes heated during compressor operation, the temperature of thelubricant 39 is raised such that condensed refrigerant fluid mixed with thelubricant 39 is vaporized for use by the suction side of the compressor. This removal of refrigerant from thesump lubricant 39 helps prevent the introduction of liquid refrigerant into the bearings associated with the crankshaft and motor shaft, which is undesirable, thereby minimizing the possibility of premature failure of the bearings. Additionally, since remainingportion 120 is at least partially, if not totally, submerged bylubricant 39, this maintained intimate contact with thelubricant 39 provides improved pressure pules attenuation as compared to an identical length of remainingportion 120 that is exposed only to refrigerant vapor. - While the invention has been described with reference to a preferred embodiment, it will be understood by those skilled in the art that various changes may be made and equivalents may be substituted for elements thereof without departing from the scope of the invention. In addition, many modifications may be made to adapt a particular situation or material to the teachings of the invention without departing from the essential scope thereof. Therefore, it is intended that the invention not be limited to the particular embodiment disclosed as the best mode contemplated for carrying out this invention, but that the invention will include all embodiments falling within the scope of the appended claims.
Claims (17)
1. A discharge muffler system for use in a refrigerant compressor, the discharge muffler system comprising:
a tube having a first end for receiving a flow of pressurized refrigerant fluid and a second end opposite the first end for exhausting the flow of pressurized refrigerant fluid;
a housing surrounding the tube between the first end and the second end, the housing and the tube defining a chamber therebetween, the chamber being in fluid communication with the flow of pressurized refrigerant fluid;
a pressure relief member connected to the housing and being configured and disposed to regulate fluid pressure in the chamber;
wherein the pressure relief member regulates pressure in the chamber by actuating to an open position to vent a portion of the refrigerant fluid from the chamber in response to a pressure in the chamber exceeding a predetermined pressure level; and
a unitary discharge tube connected to the second end of the tube to receive the flow of pressurized refrigerant fluid.
2. The discharge muffler system of claim 1 wherein the tube, the housing and the chamber form an acoustic muffler.
3. The discharge muffler system of claim 1 wherein the tube comprises at least two apertures disposed within the housing between the first end of the tube and the second tube of the tube, the at least two apertures being configured to permit flow of refrigerant fluid from the tube to the chamber.
4. The discharge muffler system of claim 3 wherein the tube has a substantially vertical orientation upon installation of the tube and at least one aperture of the at least two apertures is configured and disposed to provide a maximum level of a lubricant liquid received from the first end of the tube.
5. The discharge muffler system of claim 4 wherein the maximum level of the lubricant liquid does not substantially alter an attenuation frequency of a muffler formed from the tube, the housing and the chamber.
6. The discharge muffler system of claim 1 comprising a discharge port to exhaust the flow of pressurized refrigerant fluid from the refrigerant compressor and an end of the unitary discharge tube is connected to the discharge port and a portion of the unitary discharge tube extends substantially coplanar with the discharge port.
7. The discharge muffler system of claim 1 wherein a portion of the unitary discharge tube is in thermal communication with an amount of sump lubricant in the refrigerant compressor.
8. The discharge muffler system of claim 7 wherein the thermal communication vaporizes at least a portion of refrigerant liquid in the sump lubricant.
9. The discharge muffler system of claim 1 wherein a portion of the unitary discharge tube is in physical contact with an amount of sump lubricant in the refrigerant compressor.
10. The discharge muffler system of claim 9 wherein the physical contact between the unitary discharge tube and the sump lubricant provides an amount of pressure pulse attenuation.
11. The discharge muffler system of claim 1 wherein the second end of the tube and the connection between the second end of the tube and the unitary discharge tube are substantially coaxial.
12. A method for assembling a discharge muffler system for use in a refrigerant compressor, the steps comprising:
providing a discharge muffler having a muffler housing, an intake tube at a first end of the muffler housing for receiving a flow of refrigerant fluid and an exhaust tube at a second end of the muffler housing opposite the first end to exhaust the flow of refrigerant fluid, the intake tube being configured for connection with a cylinder head of a refrigerant compressor, and the intake tube, the exhaust tube and the connection with the cylinder head being substantially coaxial;
providing a discharge tube having an intake for connection to the exhaust tube and having an exhaust for connection to a discharge port of the refrigerant compressor, the discharge tube transporting the flow of refrigerant fluid from the exhaust tube to the discharge port for discharging the refrigerant fluid from the compressor;
providing a driving tool for connecting the discharge muffler to the cylinder head, the driving tool having an aperture;
directing the aperture of the driving tool over the exhaust tube until the driving tool and the discharge muffler are sufficiently engaged, wherein the discharge muffler is actuated in response to an actuating force being applied to the driving tool;
directing the intake tube of the discharge muffler in engagement with the driving tool into mutual alignment with the cylinder head;
applying the actuating force to the driving tool until the discharge muffler is connected to the cylinder head;
connecting the second end to the intake; and
connecting the exhaust to the discharge port.
13. The method of claim 12 wherein discharge muffler includes a pressure relief member, the muffler housing having a boss formed therein to structurally carry the pressure relief member, and the pressure relief member and the intake tube being in fluid communication; and
the step of directing the aperture of the driving tool over the exhaust tube further comprising the step of directing the aperture of the driving tool over the exhaust tube until the boss and the driving tool are sufficiently engaged.
14. A discharge muffler system for use in a refrigerant compressor, comprising:
a muffler housing;
an intake tube disposed at a first end of the muffler housing for receiving a flow of pressurized refrigerant fluid from a connection with a cylinder head of a refrigerant compressor, the intake tube and the connection with the cylinder head being substantially coaxial;
an exhaust tube disposed at a second end of the muffler housing opposite the first end of the muffler housing to exhaust the flow of pressurized refrigerant fluid, the muffler housing surrounding the intake tube and the exhaust tube between the first end and the second end to define a chamber therebetween, the chamber being in fluid communication with the refrigerant fluid flowing in the intake tube, and the intake tube and the exhaust tube being substantially coaxial;
a pressure relief member connected to the housing and being configured and disposed to regulate fluid pressure in the chamber; and
wherein the pressure relief member regulates pressure in the chamber by actuating to an open position in response to a pressure in the chamber exceeding a predetermined pressure level to vent a portion of the refrigerant fluid in the chamber to an exterior of the housing; and
a unitary discharge tube receiving the flow of pressurized refrigerant fluid from the exhaust tube and exhausting the flow of the pressurized refrigerant fluid from the refrigerant compressor.
15. The discharge muffler system of claim 14 wherein a muffler comprising the intake tube, the exhaust tube, the muffler housing and the chamber is an acoustic muffler.
16. The discharge muffler system of claim 14 wherein the intake tube and the exhaust tube are integral and continuous, defining a combined tube.
17. The discharge muffler system of claim 16 wherein the combined tube comprises at least two apertures disposed within the housing between the first end of the combined tube and the second tube of the combined tube, the at least two apertures being configured to permit flow of refrigerant fluid from the combined tube to the chamber.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/440,763 US20040234386A1 (en) | 2003-05-19 | 2003-05-19 | Discharge muffler having an internal pressure relief valve |
PCT/US2004/014872 WO2004104494A2 (en) | 2003-05-19 | 2004-05-13 | Discharge muffler having an internal pressure relief valve |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/440,763 US20040234386A1 (en) | 2003-05-19 | 2003-05-19 | Discharge muffler having an internal pressure relief valve |
Publications (1)
Publication Number | Publication Date |
---|---|
US20040234386A1 true US20040234386A1 (en) | 2004-11-25 |
Family
ID=33449861
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/440,763 Abandoned US20040234386A1 (en) | 2003-05-19 | 2003-05-19 | Discharge muffler having an internal pressure relief valve |
Country Status (2)
Country | Link |
---|---|
US (1) | US20040234386A1 (en) |
WO (1) | WO2004104494A2 (en) |
Cited By (8)
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US20080145242A1 (en) * | 2006-12-01 | 2008-06-19 | Seibel Stephen M | Dual chamber discharge muffler |
US20080166252A1 (en) * | 2006-12-01 | 2008-07-10 | Christopher Stover | Compressor with discharge muffler |
US20090038684A1 (en) * | 2007-08-09 | 2009-02-12 | Optimum Power Technology L.P. | Pulsation Attenuation |
US20100111713A1 (en) * | 2007-08-09 | 2010-05-06 | Optimum Power Technology L.P. | Apparatuses, systems, and methods for improved performance of a pressurized system |
US20140212307A1 (en) * | 2013-01-25 | 2014-07-31 | Bristol Compressors International, Inc. | Apparatus and method for connecting a compressor to a system |
US20140212310A1 (en) * | 2013-01-25 | 2014-07-31 | Bristol Compressors International, Inc. | Suction filter for a compressor |
US20150300337A1 (en) * | 2011-12-23 | 2015-10-22 | Gea Bock Gmbh | Compressor |
EP3633192A1 (en) * | 2018-10-01 | 2020-04-08 | Nidec Global Appliance Austria GmbH | Coolant compressor |
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Cited By (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20080145242A1 (en) * | 2006-12-01 | 2008-06-19 | Seibel Stephen M | Dual chamber discharge muffler |
US20080166252A1 (en) * | 2006-12-01 | 2008-07-10 | Christopher Stover | Compressor with discharge muffler |
US8057194B2 (en) | 2006-12-01 | 2011-11-15 | Emerson Climate Technologies, Inc. | Compressor with discharge muffler attachment using a spacer |
US9404499B2 (en) | 2006-12-01 | 2016-08-02 | Emerson Climate Technologies, Inc. | Dual chamber discharge muffler |
US20090038684A1 (en) * | 2007-08-09 | 2009-02-12 | Optimum Power Technology L.P. | Pulsation Attenuation |
US20100111713A1 (en) * | 2007-08-09 | 2010-05-06 | Optimum Power Technology L.P. | Apparatuses, systems, and methods for improved performance of a pressurized system |
US9567996B2 (en) | 2007-08-09 | 2017-02-14 | OPTIMUM Pumping Technology, Inc. | Pulsation attenuation |
CN102317626B (en) * | 2009-01-12 | 2016-01-20 | 最佳动力技术有限合伙公司 | For improving device, the system and method for the performance of pressurizing system |
CN105443353A (en) * | 2009-01-12 | 2016-03-30 | 最佳动力技术有限合伙公司 | Apparatus, system, and method for improved performance of a pressurized system |
WO2010081148A3 (en) * | 2009-01-12 | 2010-09-10 | Optimum Power Technology L.P. | Apparatuses, systems, and methods for improved performance of a pressurized system |
US20150300337A1 (en) * | 2011-12-23 | 2015-10-22 | Gea Bock Gmbh | Compressor |
US20140212310A1 (en) * | 2013-01-25 | 2014-07-31 | Bristol Compressors International, Inc. | Suction filter for a compressor |
US20140212307A1 (en) * | 2013-01-25 | 2014-07-31 | Bristol Compressors International, Inc. | Apparatus and method for connecting a compressor to a system |
EP3633192A1 (en) * | 2018-10-01 | 2020-04-08 | Nidec Global Appliance Austria GmbH | Coolant compressor |
Also Published As
Publication number | Publication date |
---|---|
WO2004104494A3 (en) | 2005-06-30 |
WO2004104494A2 (en) | 2004-12-02 |
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Legal Events
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AS | Assignment |
Owner name: BRISTOL COMPRESSORS, INC., VIRGINIA Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:CHUMLEY, EUGENE KARL;MARSHALL, STEVE EDWIN;MONK, DAVID TURNER;AND OTHERS;REEL/FRAME:014094/0811 Effective date: 20030515 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |