US20070140872A1 - Compressor assembly for air conditioner system - Google Patents
Compressor assembly for air conditioner system Download PDFInfo
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- US20070140872A1 US20070140872A1 US11/610,810 US61081006A US2007140872A1 US 20070140872 A1 US20070140872 A1 US 20070140872A1 US 61081006 A US61081006 A US 61081006A US 2007140872 A1 US2007140872 A1 US 2007140872A1
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- ball
- piston
- compressor assembly
- set forth
- hole
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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
- 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
- F04B49/035—Bypassing
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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
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
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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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
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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
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
- F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
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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
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/28—Safety arrangements; Monitoring
Definitions
- the invention relates to air conditioning or heat pump systems. More particularly, the invention relates to a compressor assembly for use in an air conditioning or heat pump system.
- a pressure relief valve is typically used between the discharge chamber and the suction chamber (inside a hermetic shell) of the compressor.
- the pressure relief valve opens when the differential pressure exceeds a predetermined nominal value, e.g. less than the burst pressure of the hermetic shell.
- a predetermined nominal value e.g. less than the burst pressure of the hermetic shell.
- the relief valve may be kept open by the flow of liquid, or vapor and liquid, or cool vapor refrigerant causing insufficient temperature rise in the motor windings to trip the thermal overload.
- a compressor assembly for an air conditioning system.
- the compressor assembly includes a housing generally enclosing a discharge chamber and a suction chamber.
- the compressor assembly also includes a valve operative for controlling the pressure differential between the discharge and suction chambers.
- the valve includes a body, a piston, a spring and a ball.
- the body has a first passage and a second passage in fluid communication with the first passage.
- the piston is slidably coupled to the body for axial movement between a closed position and an open position.
- the spring continuously biases the piston toward the closed position.
- the ball is fixedly secured to the piston for movement therewith between the closed position, wherein the ball engages the body to prevent a fluid flow between the first and second passages, and the open position, wherein the ball is spaced apart from the body to allow the fluid flow between the first and second passages.
- the ball is fixedly secured to the piston to prevent erosion due to relative movement and contact between the ball and the piston.
- an air conditioning system includes a condenser, an expansion valve, an evaporator and a compressor assembly.
- the compressor assembly includes a housing and a pressure relief valve.
- the housing generally encloses a discharge chamber and a suction chamber.
- the valve is operative for controlling the pressure differential between the discharge and suction chambers.
- the valve includes a body, a ball and a piston.
- the body has a first passage and a second passage in fluid communication with the first passage.
- the piston is slidably coupled to the body for axial movement between a closed position and an open position. The piston is continuously biased toward the closed position.
- the piston includes a hole for supporting the ball therein for movement with the piston between the closed position, wherein the ball engages the body to prevent fluid flow between the first and second passages, and the open position, wherein the ball is spaced apart from the body to allow fluid flow between the first and second passages.
- the ball is fixedly secured to the piston to prevent erosion due to relative movement and contact between the ball and the piston.
- FIG. 1 is a schematic view of an air conditioning system according to the invention
- FIG. 2 is a cross sectional view of a compressor assembly of the air conditioning system according the invention.
- FIG. 3 is an enlarged cross sectional view of the compressor assembly of FIG. 2 ;
- FIG. 4 is a cross sectional view of a valve in the compressor assembly of FIG. 3 shown in the open position
- FIG. 5 is a cross sectional view of the valve in the closed position.
- an air conditioning system for cooling the air in a generally enclosed environment is generally indicated at 2.
- the system includes a compressor 4 , a condenser 6 , an expansion device 14 and an evaporator 16 .
- the compressor 4 compresses a refrigerant gas to high pressure, which causes the gas to become hot.
- the hot high pressure gas exits the compressor 4 and enters the condenser 6 , where it dissipates heat and condenses into a high pressure liquid.
- the liquid moves from the condenser 6 to an expansion device 14 via a liquid line 12 .
- the liquid filters through a filter drier 13 prior to entering the expansion device 14 .
- the liquid passes through the expansion device 14 and into the evaporator 16 , where it evaporates to a vapor or gas state. Heat is absorbed from the air surrounding the evaporator due to the evaporation process, thereby cooling the enclosed environment.
- the gas returns to the compressor 4 via a suction line 18 to begin another refrigeration cycle.
- the compressor 4 includes a high-pressure discharge chamber 3 and a low-pressure suction chamber 5 .
- the compressor 4 in the illustrated embodiment is a scroll compressor, which utilizes a pair of spiral-shaped scrolls 7 , 9 fit together to form generally crescent-shaped gas pockets.
- One of the scrolls is a fixed scroll 7 and remains stationary, while the other is an orbiting scroll 9 that moves in a spiral manner about the fixed scroll 7 .
- the orbiting scroll 9 is driven by an internal motor 11 via a crankshaft 15 . Gas from the suction chamber 5 is drawn into an outer pocket created by the two scrolls 7 , 9 . As the spiral motion continues, the gas is forced toward the center of the fixed scroll 7 .
- the volume of the pocket becomes continuously smaller toward the center, thereby compressing the gas.
- the compressed gas reaches the center of the fixed scroll 7 , it is discharged into the discharge chamber 3 and recirculated in the refrigeration cycle as described above.
- other types of compressors such as a reciprocating piston-type compressor.
- a channel 17 is formed in the fixed scroll 7 and extends between the discharge chamber 3 and the suction chamber 5 .
- a pressure relief valve 10 is threaded into the channel 17 of the fixed scroll 7 .
- the valve 10 may also be fixedly secured to the fixed scroll 7 by welding, or other suitable fixing methods.
- the pressure relief valve 10 is movable between a closed position in FIG. 5 and an open position in FIG. 4 for regulating the pressure differential between the chambers 3 , 5 during operation of the compressor 4 .
- the valve 10 includes a body 20 , a piston 30 , a biasing spring 40 and a ball 50 .
- a cylindrical bore 22 extends through an end of the body 20 for slidably supporting the piston 30 therein.
- a first passage 24 extends through an opposite end of the body 20 and is coaxial with the bore 22
- a second passage 26 extends through the body 20 along an axis generally orthogonal to the first passage 24 .
- the piston 30 includes a first hole 32 formed at one end and a second hole 34 formed at an opposite end.
- a center bore 35 extends axially between the first 32 and second 34 holes.
- the center bore 35 has a smaller diameter than both the first 32 and second 34 holes, thereby defining opposite and annular-shaped first and second end walls 36 , 38 .
- the spring 40 is compressed between the first end wall 36 and a flange 39 formed near the opening of the bore 22 for continuously axially biasing the piston 30 toward the closed position shown in FIG. 5 .
- the ball 50 is fixedly secured to the piston 30 to prevent spinning of the ball 50 at the seat 49 . More specifically, an annular lip or seat 49 is defined at the intersection between the walls of the center bore 35 and the second end wall 38 . A portion of the ball 50 abuts the seat 49 and is press or interference fit in the second hole 34 of the piston 30 . The interference fit prevents rotation of the ball 50 relative to the piston 30 as fluid passes through the passages 24 , 26 when the valve is in the open position, as shown in FIGS. 2 and 4 , thereby minimizing erosion or wear of the ball 50 and piston 40 surfaces.
- the ball 50 is disposed in the second hole 34 and welded to the piston 30 .
- the weld is achieved utilizing a high current density projection weld process.
- the weld prevents the ball 50 from rotating relative to the piston 30 as fluid passes through the passages 24 , 26 when the valve is in the open position.
- the welding of the ball 50 to the piston 30 minimizes erosion or wear of the ball 50 and piston 40 surfaces.
- the ball 50 In use, the ball 50 is maintained in the closed position due to the axial force applied by the spring 40 between the piston 30 and the flange 39 of the body 20 . Fluid flow between the first 24 and second 26 channels is prevented by the ball 50 in the closed position.
- a predetermined pressure level generally determined by the spring constant of the spring 40
- the piston 30 and ball 50 are displaced from the closed position toward the open position. Once the ball 50 is in the open position, fluid can pass between the first 24 and second 26 passages, thereby relieving pressure in the first passage 24 .
- the ball 50 being fixedly secured in the second hole 34 of the piston 30 is prevented from spinning due to the flow of fluid passing between the first 24 and second 26 passages. Once the pressure is relieved, the spring 40 forces the piston 30 and ball 50 to the closed position to prevent further fluid flow between the passages 24 , 26 .
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Compressor (AREA)
Abstract
An air conditioning system includes a compressor assembly having a housing and a valve. The housing generally encloses a discharge chamber and a suction chamber. The valve is operative for controlling the pressure differential between the discharge and suction chambers. The valve includes a body, a ball, spring, flange and a piston. The body has a first passage and a second passage in fluid communication with the first passage. The piston is slidably coupled to the body for axial movement between a closed position and an open position. The piston includes a hole for supporting the ball therein for movement with the piston between the closed position, wherein the ball engages the body to prevent fluid flow between the first and second passages, and the open position, wherein the ball is spaced apart from the body to allow fluid flow between the first and second passages. The ball is fixedly secured to the piston to prevent erosion due to relative movement and contact between the ball and the piston
Description
- This application claims priority to U.S. provisional patent application No. 60/751,100 filed Dec. 16, 2005 and 60/777,422 filed on Feb. 27, 2006, which are incorporated herein by reference in their entirety.
- The invention relates to air conditioning or heat pump systems. More particularly, the invention relates to a compressor assembly for use in an air conditioning or heat pump system.
- In an air conditioning or heat pump system having a hermetic compressor, condenser, evaporator and expansion device, a problem exists when the condenser fan fails, functions intermittently, or when the condenser surface is restricted so that adequate air flow across the surface does not allow the refrigerant to condense to liquid. As a result, the gas returns to the compressor at a much higher pressure/temperature than under normal operating conditions. The compressor continues to run, thereby re-compressing the gas to an even higher pressure/temperature and creating a high pressure safety condition.
- To circumvent this issue a pressure relief valve is typically used between the discharge chamber and the suction chamber (inside a hermetic shell) of the compressor. The pressure relief valve opens when the differential pressure exceeds a predetermined nominal value, e.g. less than the burst pressure of the hermetic shell. As the compressor continues to run, the internal temperature rises until a thermal overload circuit located in the compressor motor windings trips and disconnects the electrical circuit. This causes the compressor to shut-down until the temperature of the motor windings falls below a reset point of the overload. As this point is reached the compressor restarts and the cycle begins again. Due to the complexity of the heat pump systems reversing the role of the evaporator and condenser, and/or the location of the thermal overload in the motor windings in relation to the pressure relief valve discharge ports, the relief valve may be kept open by the flow of liquid, or vapor and liquid, or cool vapor refrigerant causing insufficient temperature rise in the motor windings to trip the thermal overload.
- In conventional pressure relief valves utilizing a ball/piston interface, a clearance fit is provided between the ball and the piston for ease of assembly. However under the conditions discussed above when refrigerant is being pumped through the relief valve holding the valve wide open, the ball is free to spin in a socket form in the piston. Under continuous run conditions the spinning of the ball erodes the piston at the socket. Test and field failure samples have shown that the ball will eventually erode into, or through the piston rendering the pressure relief valve inoperative, i.e. wide open, while permitting continuous compressor operation without providing any cooling.
- Thus, it remains desirable to provide an air conditioning system with an improved compressor which overcomes the shortcomings of the aforementioned conventional air conditioning systems.
- According to one aspect of the invention, a compressor assembly is provided for an air conditioning system. The compressor assembly includes a housing generally enclosing a discharge chamber and a suction chamber. The compressor assembly also includes a valve operative for controlling the pressure differential between the discharge and suction chambers. The valve includes a body, a piston, a spring and a ball. The body has a first passage and a second passage in fluid communication with the first passage. The piston is slidably coupled to the body for axial movement between a closed position and an open position. The spring continuously biases the piston toward the closed position. The ball is fixedly secured to the piston for movement therewith between the closed position, wherein the ball engages the body to prevent a fluid flow between the first and second passages, and the open position, wherein the ball is spaced apart from the body to allow the fluid flow between the first and second passages. The ball is fixedly secured to the piston to prevent erosion due to relative movement and contact between the ball and the piston.
- According to another aspect of the invention, an air conditioning system includes a condenser, an expansion valve, an evaporator and a compressor assembly. The compressor assembly includes a housing and a pressure relief valve. The housing generally encloses a discharge chamber and a suction chamber. The valve is operative for controlling the pressure differential between the discharge and suction chambers. The valve includes a body, a ball and a piston. The body has a first passage and a second passage in fluid communication with the first passage. The piston is slidably coupled to the body for axial movement between a closed position and an open position. The piston is continuously biased toward the closed position. The piston includes a hole for supporting the ball therein for movement with the piston between the closed position, wherein the ball engages the body to prevent fluid flow between the first and second passages, and the open position, wherein the ball is spaced apart from the body to allow fluid flow between the first and second passages. The ball is fixedly secured to the piston to prevent erosion due to relative movement and contact between the ball and the piston.
- Advantages of the present invention will be readily appreciated as the same becomes better understood by reference to the following detailed description when considered in connection with the accompanying drawings, wherein:
-
FIG. 1 is a schematic view of an air conditioning system according to the invention; -
FIG. 2 is a cross sectional view of a compressor assembly of the air conditioning system according the invention; -
FIG. 3 is an enlarged cross sectional view of the compressor assembly ofFIG. 2 ; -
FIG. 4 is a cross sectional view of a valve in the compressor assembly ofFIG. 3 shown in the open position; and -
FIG. 5 is a cross sectional view of the valve in the closed position. - Referring to
FIG. 1 , an air conditioning system for cooling the air in a generally enclosed environment is generally indicated at 2. The system includes acompressor 4, acondenser 6, anexpansion device 14 and anevaporator 16. Thecompressor 4 compresses a refrigerant gas to high pressure, which causes the gas to become hot. The hot high pressure gas exits thecompressor 4 and enters thecondenser 6, where it dissipates heat and condenses into a high pressure liquid. The liquid moves from thecondenser 6 to anexpansion device 14 via aliquid line 12. Optionally, the liquid filters through afilter drier 13 prior to entering theexpansion device 14. The liquid passes through theexpansion device 14 and into theevaporator 16, where it evaporates to a vapor or gas state. Heat is absorbed from the air surrounding the evaporator due to the evaporation process, thereby cooling the enclosed environment. The gas returns to thecompressor 4 via asuction line 18 to begin another refrigeration cycle. - Referring now to
FIGS. 2-3 , thecompressor 4 includes a high-pressure discharge chamber 3 and a low-pressure suction chamber 5. Thecompressor 4 in the illustrated embodiment is a scroll compressor, which utilizes a pair of spiral-shaped scrolls fixed scroll 7 and remains stationary, while the other is anorbiting scroll 9 that moves in a spiral manner about thefixed scroll 7. The orbitingscroll 9 is driven by aninternal motor 11 via acrankshaft 15. Gas from thesuction chamber 5 is drawn into an outer pocket created by the twoscrolls fixed scroll 7. The volume of the pocket becomes continuously smaller toward the center, thereby compressing the gas. When the compressed gas reaches the center of thefixed scroll 7, it is discharged into thedischarge chamber 3 and recirculated in the refrigeration cycle as described above. Optionally, other types of compressors may be used, such as a reciprocating piston-type compressor. - A
channel 17 is formed in the fixedscroll 7 and extends between thedischarge chamber 3 and thesuction chamber 5. Apressure relief valve 10 is threaded into thechannel 17 of the fixedscroll 7. Thevalve 10 may also be fixedly secured to the fixedscroll 7 by welding, or other suitable fixing methods. Thepressure relief valve 10 is movable between a closed position inFIG. 5 and an open position inFIG. 4 for regulating the pressure differential between thechambers compressor 4. - The
valve 10 includes abody 20, apiston 30, a biasingspring 40 and aball 50. Acylindrical bore 22 extends through an end of thebody 20 for slidably supporting thepiston 30 therein. Afirst passage 24 extends through an opposite end of thebody 20 and is coaxial with the bore 22 Asecond passage 26 extends through thebody 20 along an axis generally orthogonal to thefirst passage 24. - The
piston 30 includes afirst hole 32 formed at one end and asecond hole 34 formed at an opposite end. A center bore 35 extends axially between the first 32 and second 34 holes. The center bore 35 has a smaller diameter than both the first 32 and second 34 holes, thereby defining opposite and annular-shaped first andsecond end walls - The
spring 40 is compressed between thefirst end wall 36 and aflange 39 formed near the opening of thebore 22 for continuously axially biasing thepiston 30 toward the closed position shown inFIG. 5 . - The
ball 50 is fixedly secured to thepiston 30 to prevent spinning of theball 50 at theseat 49. More specifically, an annular lip orseat 49 is defined at the intersection between the walls of the center bore 35 and thesecond end wall 38. A portion of theball 50 abuts theseat 49 and is press or interference fit in thesecond hole 34 of thepiston 30. The interference fit prevents rotation of theball 50 relative to thepiston 30 as fluid passes through thepassages FIGS. 2 and 4 , thereby minimizing erosion or wear of theball 50 andpiston 40 surfaces. - In a second embodiment, the
ball 50 is disposed in thesecond hole 34 and welded to thepiston 30. The weld is achieved utilizing a high current density projection weld process. As in the previous embodiment, the weld prevents theball 50 from rotating relative to thepiston 30 as fluid passes through thepassages ball 50 to thepiston 30 minimizes erosion or wear of theball 50 andpiston 40 surfaces. - In use, the
ball 50 is maintained in the closed position due to the axial force applied by thespring 40 between thepiston 30 and theflange 39 of thebody 20. Fluid flow between the first 24 and second 26 channels is prevented by theball 50 in the closed position. When the pressure in thefirst passage 24 exceeds a predetermined pressure level, generally determined by the spring constant of thespring 40, thepiston 30 andball 50 are displaced from the closed position toward the open position. Once theball 50 is in the open position, fluid can pass between the first 24 and second 26 passages, thereby relieving pressure in thefirst passage 24. Theball 50 being fixedly secured in thesecond hole 34 of thepiston 30 is prevented from spinning due to the flow of fluid passing between the first 24 and second 26 passages. Once the pressure is relieved, thespring 40 forces thepiston 30 andball 50 to the closed position to prevent further fluid flow between thepassages - The invention has been described in an illustrative manner. It is, therefore, to be understood that the terminology used is intended to be in the nature of words of description rather than of limitation. Many modifications and variations of the invention are possible in light of the above teachings. For example, the air conditioning system described above may also be operated as a heat pump incorporating the compressor assembly and pressure relief valve as described herein. Thus, within the scope of the appended claims, the invention may be practiced other than as specifically described.
Claims (21)
1. A compressor assembly for an air conditioning system, said compressor assembly comprising:
a housing generally enclosing a discharge chamber and a suction chamber; and
a valve operative for controlling the pressure differential between the discharge and suction chambers, the valve having:
a body having a first passage and a second passage in fluid communication with the first passage;
a piston slidably coupled to the body for axial movement between a closed position and an open position;
a spring continuously biasing the piston toward the closed position; and
a ball movable with the piston between the closed position, wherein the ball engages the body to prevent fluid flow between the first and second passages, and the open position, wherein the ball is spaced apart from the body to allow fluid flow between the first and second passages, the ball being fixedly secured to the piston to prevent erosion due to relative movement and contact between the ball and the piston.
2. A compressor assembly as set forth in claim 1 , wherein the piston includes a generally cylindrical hole for supporting the ball therein.
3. A compressor assembly as set forth in claim 2 , wherein the ball is press fit in the hole to prevent the ball from spinning relative to the piston.
4. A compressor assembly as set forth in claim 2 , wherein the ball is disposed in the hole and welded to the piston.
5. A compressor assembly as set forth in claim 4 , wherein the weld is formed by a high current density projection weld.
6. A compressor assembly as set forth in claim 2 , wherein the piston includes a center bore having a smaller diameter than the hole, the center bore being substantially axially aligned with and adjacent to the hole to define an annular seat.
7. A compressor assembly as set forth in claim 6 , wherein the ball abuts the seat.
8. A compressor assembly as set forth in claim 7 , wherein the ball is disposed in the hole and welded to the piston.
9. A compressor assembly as set forth in claim 9 , wherein the weld is formed by a high current density projection weld.
10. A compressor assembly as set forth in claim 7 , wherein the ball is press fit in the hole to prevent the ball from spinning relative to the piston.
11. A compressor assembly as set forth in claim 10 , wherein the first and second passages are generally orthogonal relative to each other.
12. A compressor assembly as set forth in claim 11 , wherein the piston moves between the closed and open positions along an axis generally aligned with a longitudinal axis of one of the first and second passages.
13. A compressor assembly as set forth in claim 12 , wherein the ball in the closed position abuts an opening of the one of the first and second passages to prevent fluid flow between the first and second passages.
14. A compressor assembly as set forth in claim 13 , wherein the hole, center bore and the one of the first and second passages are generally coaxially aligned.
15. An air conditioning system comprising:
a condenser;
an expansion device;
an evaporator; and
a compressor assembly having a housing and a pressure relief valve, the housing generally enclosing a discharge chamber and a suction chamber, the valve being operative for controlling the pressure differential between the discharge and suction chambers, the valve including:
a body having a first passage and a second passage in fluid communication with the first passage;
a ball; and
a piston slidably coupled to the body for axial movement between a closed position and an open position, the piston being continuously biased toward the closed position, the piston having a hole for supporting the ball therein for movement with the piston between the closed position, wherein the ball engages the body to prevent fluid flow between the first and second passages, and the open position, wherein the ball is spaced apart from the body to allow fluid flow between the first and second passages, the ball being fixedly secured to the piston to prevent erosion due to relative movement and contact between the ball and the piston.
16. A compressor assembly as set forth in claim 15 , wherein the ball is press fit in the hole to prevent the ball from spinning relative to the piston.
17. A compressor assembly as set forth in claim 15 , wherein the ball is welded to the piston.
18. A compressor assembly as set forth in claim 17 , wherein the weld is formed by a high current density projection weld.
19. A compressor assembly as set forth in claim 15 , wherein the piston includes a center bore having a smaller diameter than the hole, the center bore being substantially axially aligned with and adjacent to the hole to define an annular seat.
20. A compressor assembly as set forth in claim 19 , wherein the ball abuts the seat and is press fit in the hole to prevent relative movement between the ball from and the piston.
21. A compressor assembly as set forth in claim 19 , wherein the ball abuts the seat and is welded to the piston to prevent relative movement between the ball from and the piston.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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US11/610,810 US20070140872A1 (en) | 2005-12-16 | 2006-12-14 | Compressor assembly for air conditioner system |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
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US75110005P | 2005-12-16 | 2005-12-16 | |
US77742206P | 2006-02-27 | 2006-02-27 | |
US11/610,810 US20070140872A1 (en) | 2005-12-16 | 2006-12-14 | Compressor assembly for air conditioner system |
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US20070140872A1 true US20070140872A1 (en) | 2007-06-21 |
Family
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US11/610,810 Abandoned US20070140872A1 (en) | 2005-12-16 | 2006-12-14 | Compressor assembly for air conditioner system |
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Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150118076A1 (en) * | 2013-10-31 | 2015-04-30 | Emerson Climate Technologies, Inc. | Compressor with improved valve assembly |
CN110691911A (en) * | 2017-06-06 | 2020-01-14 | 三菱电机株式会社 | Scroll compressor and refrigeration cycle device |
WO2024031787A1 (en) * | 2022-08-12 | 2024-02-15 | 深圳昂湃技术有限公司 | Pressure balance structure of carbon dioxide scroll compressor |
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US5690475A (en) * | 1993-12-28 | 1997-11-25 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor with overload protection |
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US6622752B2 (en) * | 2000-06-16 | 2003-09-23 | Bosch Automotive Systems Corporation | Pressure relief valve |
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US7311118B2 (en) * | 2004-03-30 | 2007-12-25 | Parker-Hannifin Corporation | Floating ball check valve |
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2006
- 2006-12-14 US US11/610,810 patent/US20070140872A1/en not_active Abandoned
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US4552312A (en) * | 1983-01-14 | 1985-11-12 | Tohoku Mikuni Kogyo Kabushiki Kaisha | Fuel injection valve |
US5362210A (en) * | 1993-02-26 | 1994-11-08 | Tecumseh Products Company | Scroll compressor unloader valve |
US5690475A (en) * | 1993-12-28 | 1997-11-25 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor with overload protection |
US5503542A (en) * | 1995-01-13 | 1996-04-02 | Copeland Corporation | Compressor assembly with welded IPR valve |
US6622752B2 (en) * | 2000-06-16 | 2003-09-23 | Bosch Automotive Systems Corporation | Pressure relief valve |
US6588857B2 (en) * | 2001-09-21 | 2003-07-08 | Mando Corporation | Solenoid valve for brake systems |
US7040344B2 (en) * | 2003-06-06 | 2006-05-09 | Siemens Vdo Automotive Corporation | Pressure regulator including a fixed valve ball and method of assembling the same |
US7311118B2 (en) * | 2004-03-30 | 2007-12-25 | Parker-Hannifin Corporation | Floating ball check valve |
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US20150118076A1 (en) * | 2013-10-31 | 2015-04-30 | Emerson Climate Technologies, Inc. | Compressor with improved valve assembly |
CN110691911A (en) * | 2017-06-06 | 2020-01-14 | 三菱电机株式会社 | Scroll compressor and refrigeration cycle device |
CN110691911B (en) * | 2017-06-06 | 2022-01-04 | 三菱电机株式会社 | Scroll compressor and refrigeration cycle device |
US11248604B2 (en) * | 2017-06-06 | 2022-02-15 | Mitsubishi Electric Corporation | Scroll compressor and refrigeration cycle apparatus |
WO2024031787A1 (en) * | 2022-08-12 | 2024-02-15 | 深圳昂湃技术有限公司 | Pressure balance structure of carbon dioxide scroll compressor |
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