Patent Application
20190170128
The present invention relates to a variable displacement compressor for use in an air conditioning system for a vehicle, and more particularly to an electrically controlled suction damping device disposed in a suction port of the variable displacement compressor.
As is commonly known, variable displacement compressors having a swashplate are used in air conditioning systems of motor vehicles. Such compressors typically include at least one piston disposed in a cylinder of a cylinder block and a rotor assembly operatively coupled to a drive shaft. The swashplate is coupled to and adapted to be rotated by the rotor assembly during rotation of the drive shaft. The swashplate is variably angled relative to the drive shaft between a minimum angle of inclination and a maximum angle of inclination. Each piston slidably engages with the swashplate through a shoe as the swash plate rotates, thereby causing each piston to reciprocate within the corresponding cylinder of the cylinder block. As the angle of inclination of the swashplate is varied, so too is the displacement of each piston within each cylinder, thereby causing the flow rate of a refrigerant flowing through the compressor to vary. The flow rate varies between a maximum flow rate when the swashplate is positioned at a maximum angle of inclination relative to the drive shaft and a minimum flow rate when the swashplate is positioned at a minimum angle of inclination relative to the drive shaft.
It is not uncommon for variable displacement compressors to develop suction pulsations. The suction pressure pulsations may propagate throughout the air conditioning system. When these pressure pulsations reach certain components of the air conditioning system, such as the evaporator, the pressure pulsations may cause noise to be generated that can be heard in a passenger compartment of the vehicle.
The problem of noise generation caused by suction pulsation has previously been addressed by the addition of a suction damping device within the variable displacement compressor. The suction damping device traditionally includes a spring loaded plunger reciprocatingly disposed within a body having flow openings formed therein. The position of the plunger within the body determines a cross-sectional flow area by which the refrigerant may flow through the suction damping device during different operating modes of the variable displacement compressor.
There are two primary methods for determining the position of the plunger of the suction damping device and therefore the flow rate of the refrigerant through the suction damping device. One method includes the flow of the refrigerant entering the compressor exerting pressure on the plunger to apply a force against the biasing of the spring in contact with the plunger. The depression of the spring and subsequent repositioning of the plunger alters the cross-sectional flow area past the plunger to regulate the flow rate of the refrigerant entering the compressor. One issue present when employing this method is that the plunger typically has to be biased by a relatively stiff spring to properly control the pressure pulsations. The use of a stiff spring negatively affects the efficient operation of the compressor by causing the refrigerant to undergo an undesirably large pressure drop when exerting the pressure force on the plunger to open the suction damping device. The use of a stiff spring may also result in a lower maximum flow capacity of the compressor due to the spring preventing a full opening of the suction damping device under certain operating conditions.
The second known method includes using a known pressure difference between a crankcase chamber having the swash plate disposed therein and a suction chamber disposed downstream of the suction damping device to control a position of the plunger within the body. This approach requires the addition of flow passageways within the variable displacement compressor for communicating the refrigerant at the various different pressure values to the suction damping device in order to control the position of the plunger thereof, thereby increasing the complexity of the variable displacement compressor while also presenting additional fluid passageways in need of suitable sealing means and flow control. Such suction damping devices also utilize a spring for biasing a valve element, which may negatively cause the suction damping device to be subject to the effects of hysteresis of the spring when operating under certain conditions.
It would therefore be desirable to produce a suction damping device that minimizes noise generation in an air conditioning system by providing precise control of a variable flow area of a refrigerant flow as the refrigerant flow enters a suction port of a variable displacement compressor.
Concordant and congruous with the present invention, a suction damping device utilizing an electromagnetic device to control a variable flow area through the suction damping device has surprisingly been discovered.
According to an embodiment of the invention, a suction damping device for a variable displacement compressor comprises a rotor having a rotational axis. An aperture extends through the rotor in a direction transverse to the rotational axis thereof. The rotor is selectively rotated about the rotational axis thereof to control a flow of a fluid through the aperture of the rotor.
According to another embodiment of the invention, a variable displacement compressor is disclosed. The variable displacement compressor comprises an electrically controlled valve configured to selectively control an angle of inclination of a swashplate of the variable displacement compressor and a suction damping device including a rotor having a rotational axis. An aperture extends through the rotor in a direction transverse to the rotational axis thereof. The rotor is selectively rotated about the rotational axis thereof based on a condition of the electrically controlled valve to control a flow of a fluid through the aperture of the rotor.
According to a further embodiment of the invention, a method of controlling a variable displacement compressor is disclosed. The method comprises the steps of providing a suction damping device including a rotor having a rotational axis, an aperture extending through the rotor in a direction transverse to the rotational axis, and selectively rotating the rotor about the rotational axis thereof based on a condition of an electrically controlled valve of the variable displacement compressor to control a flow of a fluid through the aperture of the rotor.
The above, as well as other advantages of the present invention, will become readily apparent to those skilled in the art from the following detailed description of a preferred embodiment when considered in the light of the accompanying drawings in which:
The following detailed description and appended drawings describe and illustrate various exemplary embodiments of the invention. The description and drawings serve to enable one skilled in the art to make and use the invention, and are not intended to limit the scope of the invention in any manner.
The rear housing 11 defines a suction chamber 15 and a discharge chamber 16. The suction chamber 15 is fluidly coupled to a suction port 5 of the compressor 10 (shown in
A drive shaft 7 is supported by the front housing 4 wherein a portion of the drive shaft 7 is disposed within the crankcase chamber 6. A swashplate 8 is mounted on the drive shaft 7 within the crankcase chamber 6 and is inclined at an angle with respect to a plane formed perpendicular to the rotational axis of the drive shaft 7. Each of the pistons 14 may be secured to the swashplate 8 by a shoe 9, which each of the shoes 9 allows for movement of the swashplate 8 relative to the pistons 14.
When the swashplate 8 is disposed at its minimum angle of inclination with respect to the plane formed perpendicular to the rotational axis of the drive shaft 7, each of the pistons 14 reciprocates to the least extent possible within each of the corresponding cylinder bores 12 as the drive shaft 7 rotates, thereby compressing a minimized volume of the refrigerant for each stroke of the corresponding piston 14. When the swashplate 8 is disposed at its greatest angle of inclination with respect to the plane formed perpendicular to the rotational axis of the drive shaft 7, the pistons 14 reciprocate in their respective cylinder bores 12 to the maximum extent, thereby compressing a maximized volume of the refrigerant for each stroke of the corresponding piston 14. As such, a flow rate of the refrigerant through the compressor 10 and hence a cooling capacity of the refrigerant exiting the compressor 10 is directly related to the angle of inclination of the swashplate 8 with respect to the plane formed perpendicular to the rotational axis of the drive shaft 7.
The angle of inclination of the swashplate 8 is selectively controlled by an electrically controlled control valve 90. The control valve 90 may generally comprise an electrical coil (not shown) for selectively positioning a valve element (not shown), wherein the valve element may be biased by one or more spring elements (not shown). The electrical coil may receive electrical power from a power source associated with the motor vehicle. The electrical coil is configured to apply an electromagnetic force to the valve element corresponding to the amount of current passing through the coil. The electromagnetic force applied to the valve element by the coil selectively positions the valve element relative to the surrounding structure of the control valve 90 and against the bias of any spring elements engaging the valve element. The amount of current passing through the coil may be determined by a control system of the motor vehicle associated with operating the compressor 10 according to the desired settings of a passenger of the motor vehicle.
The selective positioning of the valve element controls a pressure within the crankcase chamber 6 of the compressor 10, which in turn alters the angle of inclination of the swashplate 8 with respect to the plane formed perpendicular to the rotational axis of the drive shaft 7. The selective positioning of the valve element of the control valve 90 may, for example, selectively establish fluid communication between at least one of a discharge pressure of the refrigerant within the discharge chamber 16, a suction pressure of the refrigerant within the suction chamber 15, and a crankcase pressure of the refrigerant within the crankcase chamber 6. In some embodiments, additional portions of the compressor 10 having alternative pressures, such as a portion of the compressor including an oil filter or oil return passage for lubricating the compressor 10, may be in fluid communication with the crankcase chamber 6, as desired. The selective communication between the different chambers having the differing pressures may be accomplished via passageways (not shown) formed in the compressor 10 positioned to be selectively opened or closed based on the selective positioning of the valve element relative to the electrical coil and the associated passageways.
The selective positioning of the valve element of the control valve 90 allows for the pressure within the crankcase chamber 6 to be controlled in a manner wherein the amount of current passing through the coil of the control valve 90 corresponds to a generally known angle of inclination of the swashplate 8 and therefore to a generally known cooling capacity of the compressor 10. For example, the control valve 90 may be adjustable between a plurality of positions controlling flow of the refrigerant between the suction chamber 15, the discharge chamber 16, and the crankcase chamber 6 to selectively change the crankcase pressure within the crankcase chamber 6. The swashplate 8 may be configured to be disposed at a minimum angle of inclination, which corresponds to a minimal cooling capacity of the compressor 10, when the crankcase pressure within the crankcase chamber 6 is maximized. The maximizing of the crankcase pressure within the crankcase chamber 6 may be accomplished by positioning the valve element of the control valve 90 at a position maximizing an amount of the refrigerant having the discharge pressure directed into the crankcase chamber 6. The maximizing of the flow of the refrigerant having the discharge pressure into the crankcase chamber 6 may correspond to the valve element of the control valve 90 being energized with a minimal amount of current, which is referred to as Imin hereinafter. The compressor 10 operating at the minimized cooling capacity may therefore correspond to the control valve 90 being energized with the current Imin. The control valve 90 being energized with the current Imin may also correspond to the suction pressure within the suction chamber 15 being maximized at a value Pmax, as shown in
In contrast, the swashplate 8 may be configured to be disposed at a maximum angle of inclination, which corresponds to a maximum cooling capacity of the compressor 10, when the crankcase pressure within the crankcase chamber 6 is minimized. The minimizing of the crankcase pressure within the crankcase chamber 6 may be accomplished by positioning the valve element of the control valve 90 at a position minimizing an amount of the refrigerant having the discharge pressure directed into the crankcase chamber 6. The minimizing of the flow of the refrigerant having the discharge pressure into the crankcase chamber 6 may correspond to the valve element of the control valve 90 being energized with a maximum amount of current, which is referred to as Imax hereinafter. The compressor 10 operating at the maximized cooling capacity may therefore correspond to the control valve 90 being energized with the current Imax. The control valve 90 being energized with the current Imax may also correspond to the suction pressure within the suction chamber 15 being minimized at a value of Pmin, as shown in
The swashplate 8 may be positioned at a plurality of intermediate angles of inclination when the current energizing the control valve 90 is intermediate Imin and Imax. The increasing of the angle of inclination of the swashplate 8, and hence the increasing of the cooling capacity of the compressor 10, may be associated with an increasing of the current energizing the control valve 90 in order to reduce the amount of the discharge pressure communicated to the crankcase chamber 6. In contrast, the decreasing of the angle of inclination of the swashplate 8, and hence the decreasing of the cooling capacity of the compressor 10, may be associated with a decreasing of the current energizing the control valve 90 in order to increase the amount of the discharge pressure communicated to the crankcase chamber 6. The compressor 10 may accordingly be configured to have a substantially linear relationship between the angle of inclination of the swashplate 8, which corresponds to the cooling capacity of the compressor 10, and the amount of current energizing the control valve 90. However, there may alternatively be a non-linear relationship between the angle of inclination of the swashplate 8 and the current energizing the control valve 90 without departing from the scope of the present invention. The non-linear relationship may still utilize a relationship wherein an increase in the current energizing the control valve 90 corresponds to an increase in the angle of inclination of the swashplate 8 and wherein a decrease in the current energizing the control valve 90 corresponds to a decrease in the angle of inclination of the swashplate 8, as desired.
It is further understood that alternative or opposite relationships may be present between the current used to energize the control valve 90 and the angle of inclination of the swashplate 8 depending on the manner in which the control valve 90 regulates the communication between the various chambers of the compressor 10 having the differing pressures. For example, the control valve 90 may alternatively be configured wherein Imin corresponds to a maximum cooling capacity of the compressor 10, and wherein an increase in the current energizing the control valve 90 causes the cooling capacity of compressor 10 to be continuously reduced until a minimized cooling capacity of the compressor 10 is achieved when the control valve 90 is energized with the current Imax. However, it is assumed hereinafter that the minimized cooling capacity corresponds to the control valve 90 being energized with the operating current Imin, the maximized cooling capacity corresponds to the control valve 90 being energized with the operating current Imax, and wherein intermediate cooling capacities correspond to operating currents intermediate Imin and Imax.
Although the control valve 90 has generally been described as including a valve element that is moveable relative to an electrical coil and passageways associated with operation of the control valve 90, it is understood that any form of electrically controlled valve allowing for a selective adjustment of the angle of inclination of the swashplate 8 in response to the actuation of an electrically powered component may be used without departing from the scope of the present invention. Representative examples of electrically powered control valves suitable for controlling the angle of inclination of the swashplate 8 within the compressor 10 are disclosed in U.S. Pat. No. 6,390,782 to Booth et al., U.S. Pat. No. 7,014,428 to Pitla et al., U.S. Pat. No. 8,292,596 to Ota et al., and U.S. Patent Application Publication No. 2006/0083625 to Koyama et al., each of which is hereby incorporated by reference herein in its entirety.
Referring now to
The stator 30 is cylindrical in shape and includes a longitudinal axis extending in a direction perpendicular to a direction of flow of the refrigerant through the suction port 5. The stator 30 includes a substantially cylindrical hollow interior 32 configured to receive the stator 30 therein. A first opening 33 and a second opening 34 formed in an outer surface 35 of the stator 30 provide fluid communication between the hollow interior 32 and the suction port 5. The first opening 33 may be formed in facing relationship with an upstream portion of the suction port 5 with respect to the flow direction of the refrigerant while the second opening 34 may be formed in a diametrically opposed portion of the outer surface 35 of the stator 30 in facing relationship with a downstream portion of the suction port 5.
As best shown with reference to
A first end 41 of the stator 30 is received in a first opening 43 formed in a portion of the rear housing 11 defining one side of the suction port 5 while a second end 42 of the stator 30 is received in a second opening 44 formed in a portion of the rear housing 11 defining the suction port 5 diametrically opposed to the first opening 43. The second opening 44 may extend from the suction port 5 through the rear housing 11 to an exterior surface of the compressor 10 to provide access for electrical components to the SDD 20.
The stator 30 is shown and described as a separate component to be received within a portion of the rear housing 11, but it should be understood that the stator 30 may instead be formed by portions of the rear housing 11 formed in accordance with the structure of the stator 30 as shown and described herein without departing from the scope of the present invention.
The rotor 50 is substantially cylindrical in shape and is rotatably received within the stator 30. The rotor 50 includes a main body 51 extending from a first end 53 disposed adjacent the first end 41 of the stator 30 to a second end 54 disposed adjacent the second end 42 of the stator 30. A shaft 55 having a reduced diameter in comparison to the main body 51 extends axially from the second end 54 of the main body 51. The shaft 55 defines an axis of rotation of the rotor 50 arranged substantially perpendicular to the direction of flow of the refrigerant through the suction port 5 when passing through the SDD 20. One or more bearings (not shown) or similar mechanisms for allowing one component to rotate relative to another may be used at an interface between the stator 30 and the rotor 50, as desired.
The main body 51 of the rotor 50 includes an aperture 56 formed therein extending from one side of the main body 51 to a diametrically opposed side thereof The aperture 56 is shown as having a substantially elliptical or rounded rectangular cross-sectional shape, but alternative shapes may be utilized without departing from the scope of the present invention. The aperture 56 may be shaped and sized to substantially correspond in shape and size to the first and second openings 33, 34 formed in the stator 30, as desired.
The SDD 20 is actuated by an electromagnetic device 61 configured to control a rotational position of the rotor 50 relative to the stator 30. The electromagnetic device 61 may include a first electromagnetic component 62 and a second electromagnetic component 64. The first electromagnetic component 62 may be disposed within the hollow interior 32 of the stator 30 adjacent the second end 54 of the main body 51 of the rotor 50. The first electromagnetic component 62 may be annular in shape having a central opening for rotatably receiving the shaft 55 of the rotor 50. The second electromagnetic component 64 may be disposed within the shaft 55 of the rotor 50. The first electromagnetic component 62 may comprise a plurality of annularly arranged and circumferentially spaced electromagnets while the second electromagnetic component 64 may comprise a plurality of annularly arranged and circumferentially spaced permanent magnets within the shaft 55 of the rotor 50.
The first electromagnetic component 62 and the second electromagnetic component 64 may accordingly cooperate to form an electric stepper motor for precisely controlling a rotational position of the rotor 50 relative to the stator 30 by selective control of the electrical current passing through each of the electromagnets associated with the first electromagnetic component 62. It is understood that alternative electromagnetic devices 61 having alternative configurations suitable for precisely controlling the rotational position of the rotor 50 relative to the stator 30 may be utilized, as desired, without departing from the scope of the present invention. The electromagnetic device 61 may alternatively take the form of a brushless DC motor or a servo motor, as non-limiting examples of electrical actuating devices having precise rotational control.
An electrical connector 38 extends from the second end 42 of the stator 30. The electrical connector 38 provides electrical communication between the electromagnetic device 61 of the SDD 20 and a power source 95, as shown schematically in
The rotor 50 is adjustable to a plurality of rotational positions relative to the stator 30 to alter the cross-sectional flow area for the refrigerant when passing through the SDD 20.
In contrast,
The rotor 50 is configured to be selectively positioned to a plurality of different rotational positions intermediate the fully closed and the fully open positions. As the rotor 50 is rotated away from the fully closed position illustrated in
It is understood that the first opening 33 and the second opening 34 may include different shapes and sizes in a manner wherein the cross-sectional flow area present between the first opening 33 and the aperture 56 may differ from the cross-sectional flow area present between the second opening 34 and the aperture 56. Hereinafter, further reference to the cross-sectional flow area through the SDD 20 refers to the smaller of the cross-sectional flow area present between the aperture 56 and the first opening 33 and the cross-sectional flow area present between the aperture 56 and the second opening 34 as the smaller of the two cross-sectional flow areas ultimately controls the flow rate of the refrigerant through the SDD 20.
The rotational position of the rotor 50, and hence the cross-sectional flow area for the refrigerant to pass through the SDD 20, may directly correspond to the amount of current used to energize the control valve 90. For example, with reference to
As shown in
If the controller 96 determines that an increase of cooling capacity has been requested as indicated at step 220, the controller 96 next determines at a step 250 whether the control valve 90 is already operating at Imax. If the control valve 90 is already operating at Imax, the controller 96 determines that the rotational position of the rotor 50 of the SDD 20 is not to be changed at a step 260. Alternatively, if the control valve 90 is operating at a current below Imax when evaluated at step 250, the controller 96 determines and records the amount of the increase in the current requested for operating the control valve 90 in accordance with the desired cooling capacity at a step 270. Next, at a step 280, the controller 96 sends a control signal to the electromagnetic device 61 indicating that the rotor 50 of the SDD 20 is to be rotated to another rotational position indicating greater flow through the SDD 20. The new position of the rotor 50 of the SDD 20 is then recorded by the controller 96 at a step 290. As shown in
Alternatively, if the controller 96 determines that a decrease in cooling capacity has been requested as indicated at step 240, the controller 96 next determines at a step 300 whether the control valve 90 is already operating at Imin. If the control valve 90 is already operating at Imin, the controller 96 determines that the rotational position of the rotor 50 of the SDD 20 is not to be changed at a step 310 and the instantaneous rotational position of the SDD 20 is recorded at a step 340. Alternatively, if the control valve 90 is operating at a current above Imin, the controller 96 determines and records the amount of the decrease in the current requested for operating the control valve 90 in accordance with the desired cooling capacity at a step 320. Next, at a step 330, the controller 96 sends a control signal to the electromagnetic device 61 indicating that the rotor 50 of the SDD 20 is to be rotated to another rotational position indicating less flow through the SDD 20. The new position of the rotor 50 of the SDD 20 is then recorded by the controller 96 at a step 340.
The repositioning of the rotor 50 of the SDD 20 at either of steps 280 or 330 may be based on the relationship present between the current energizing the control valve 90 and the opening percentage of the SDD 20 as illustrated in
The controller 96 may include a look-up table stored to a memory thereof including an appropriate rotational positioning of the rotor 50 of the SDD 20 based on the determination of the amount of current being delivered to the control valve 90 when a passenger of the motor vehicle selects a desired cooling capacity. The look-up table may include data indicating a desired rotational position of the rotor 50 for a given current delivered to the control valve 90 in order to achieve a desired flow rate of the refrigerant through the SDD 20. The look-up table may for example include information regarding the desired rotational position of the rotor 50 for achieving a desired opening percentage of the SDD 20 for each value of the current energizing the control valve 90 between and including Imin and Imax. For example, the look-up table may include data corresponding to the relationship presented in
The controller 96 may alternatively be programmed to utilize the value of the current delivered to the control valve 90 and communicated to the controller 96 as an input value for an equation for determining a suitable rotational position of the rotor 50 based on the desired opening percentage of the SDD 20, wherein the equation may utilize a linear relationship between the current energizing the control valve 90 and the opening percentage of the SDD 20 as presented in
In use, the passenger of the motor vehicle selects an operational mode for the HVAC system requiring compression of the refrigerant passing through the compressor 10. Based on the user selected operational mode, the control valve 90 is energized by a power source to a desired position for controlling the crankcase pressure within the crankcase chamber 6, which in turn places the swashplate 8 at a desired angle of inclination corresponding to the user selected operational mode. The controller 96 receives information regarding the current being delivered to the control valve 90 and makes a determination of whether the rotor 50 of the SDD 20 is in need of repositioning as set forth in
For example, the passenger of the motor vehicle may select an operational mode wherein the compressor 10 operates with the minimized length of the stroke of each of the pistons 14 within each of the corresponding cylinder bores 12 caused by the swashplate 8 having a minimized angle of inclination with respect to the plane formed perpendicular to the rotational axis of the drive shaft 7. The selection of the operational mode having the minimized stroke length results in the power source 95 energizing the coil of the control valve 90 with the current Imin for achieving a desired crankcase pressure within the crankcase chamber 6. The controller 96 utilizes the look-up table or the equation stored to the memory thereof to determine the desired rotational position of the rotor 50 relative to the stator 30 for achieving the desired flow rate of the refrigerant through the SDD 20. The controller 96 may determine, for example, that the current Imin being passed through the electrical coil of the control valve 90 corresponds to rotating the rotor 50 relative to the stator 30 to a first rotational position having a minimized cross-sectional flow area through the SDD 20. The first rotational position may include about 10% of the cross-sectional flow area of each end of the aperture 56 exposed to each of the first opening 33 and the second opening 34 while rotating the rotor 50 to a rotational position about 10 degrees away from the fully closed position, as one non-limiting example. The controller 96 sends the control signal to the electromagnetic device 61, which accordingly repositions the rotor 50 relative to the stator 30 in accordance with the data provided by the look-up table or the equation stored to the memory of the controller 96.
As an alternative example, the passenger of the motor vehicle may desire an operational mode wherein the pistons 14 are caused to reciprocate with a maximized stroke length within each of the corresponding cylinder bores 12 caused by the swashplate 8 having a maximized angle of inclination with respect to the plane formed perpendicular to the rotational axis of the drive shaft 7. The selection of the operational mode having the maximized stroke length results in the power source 95 energizing the coil of the control valve 90 with the current Imax for achieving a desired crankcase pressure within the crankcase chamber 6. The controller 96 utilizes the look-up table stored to the memory thereof to determine the desired rotational position of the rotor 50 relative to the stator 30 for achieving the desired flow rate of the refrigerant through the SDD 20. The controller 96 may determine, for example, that the current Imax corresponds to rotating the rotor 50 to a second rotational position. The second rotational position may include about 100% of the cross-sectional flow area of the aperture 56 exposed to each of the first opening 33 and the second opening 34 while rotating the rotor 50 to the fully open position. The controller 96 sends the control signal to the electromagnetic device 61, which repositions the rotor 50 relative to the stator 30 in accordance with the data provided by the look-up table or the equation stored to the memory of the controller 96.
The look-up table or the equation of the controller 96 may be used to determine a plurality of different rotational positions of the rotor 50 intermediate the two positions discussed hereinabove to achieve a plurality of different cross-sectional flow rates through the SDD 20 depending on the desired length of stroke of each of the pistons 14 within a corresponding cylinder bore 12.
The controller 96 may also be utilized to ensure that the SDD 20 is always at a preferred position during operation of the compressor 10. For example, the controller 96 may be configured to always return the rotor 50 to a specified position, such as the fully open position or the fully closed position, following each period of use of the compressor 10 and the SDD 20. The rotational position of the rotor 50 is accordingly known when the compressor 10 and SDD 20 are first activated, thereby allowing for the rotor 50 to be rotated through a known angular displacement before arriving at the desired rotational position. Alternatively, the controller 96 may be configured to store data regarding the rotational position of the rotor 50 following each rotation thereof, thereby allowing for any subsequent rotations to be considered relative to the prior recorded rotational position. As a result, the SDD 20 is capable of precise and repeatable control of the rotational motion of the rotor 50 relative to the stator 30.
It should be understood by one skilled in the art that the variable cross-sectional flow area of the refrigerant through the SDD 20 based on the rotational position of the rotor 50 relative to the stator 30 may be achieved by various modifications of the structure of either of the rotor 50 or the stator 30. For example, the aperture 56 of the rotor 50 may alternatively include a perimeter including substantially rectilinear edges while the first opening 33 and the second opening 34 of the stator 30 may include perimeters including curvilinear edges suitable for causing a variable overlap between the aperture 56 and either of the first opening 33 and the second opening 34 during selective rotation of the rotor 50 relative to the stator 30.
It should further be understood that the general concept of utilizing rotational motion of a rotor relative to a stator to determine the cross-sectional flow area through the SDD based on the current passing through an electrically controlled control valve may alternatively be adapted for utilizing translational motion to determine the cross-sectional flow area through the SDD. For example, the rotational motion of a rotor may be transferred to the translational motion of a sliding component selectively extended across the suction port of the compressor using any known mechanism for transferring the rotational motion from one component to translational motion of another component. As the rotational position of the rotor is controlled, so to is the extent by which the sliding component extends across the suction port of the compressor for blocking the flow of the refrigerant therethrough, thereby creating a variable cross-sectional flow area through the SDD based on the rotational position of the rotor.
The desired rotational position of the rotor 50 relative to the stator 30 has been described exclusively as a function of the current caused to pass through an electrically energized component of the control valve 90, but it should be further understood that other characteristics of the compressor 10 capable of being monitored by the controller 96 and associated with the data stored to the look-up table may be utilized in the determination of the desired rotational position of the rotor 50 relative to the stator 30 without departing from the scope of the present invention. For example, the rotational position of the rotor 50 relative to the stator 30 may be a function of one or more of the suction pressure within the suction chamber 15, the discharge pressure within the discharge chamber 16, and the crankcase pressure within the crankcase chamber 6, wherein each of the associated pressure values is monitored by sensors in signal communication with the controller 96 for determining an angle of inclination of the swashplate 8. Alternatively, the controller 96 may be in signal communication with a sensor configured to directly measure the angle of inclination of the swashplate 8. Various other characteristics of the compressor 10 relating to the desired flow rate of the refrigerant entering the suction port 5 may be used to determine the desired rotational position of the rotor 50 relative to the stator 30 for each selected operational mode of the compressor 10 without departing from the scope of the present invention so long as the resulting positioning of the rotor 50 is based on a control signal indicating a condition of a portion of the compressor 10 or any components associated with the operation of the compressor 10.
The SDD 20 provides several advantages over the suction damping devices of the prior art. First, the cross-sectional flow area through the SDD 20 is controlled based on a condition of the control valve 90 known by or monitored by the controller 96, resulting in a desired configuration of the SDD 20 being communicated to the SDD 20 without requiring additional flow passageways or mechanisms within the compressor 10 for communicating various different pressures to the SDD to determine a configuration of the SDD. Second, the SDD 20 is capable of repeatable and very precise control of the flow area through the SDD by use of the electrically controlled electromagnetic device 61. Third, the manner in which the rotor 50 rotates about an axis perpendicular to the flow direction of the refrigerant allows for a maximum flow area through the SDD 20 to be achieved as the openings 33, 34 and the aperture 56 can be dimensioned to extend across an entirety of the suction port 5, as desired. Fourth, the rotational position of the rotor 50 relative to the stator 30 is capable of being fixed during use of the compressor 10, in contrast to an SDD having a plunger that is selectively repositioned based on an instantaneous pressure experienced within a portion of the compressor 10.
The main body 151 of the rotor 50 includes an aperture in the form of an indentation 156 formed therein extending from one side of the main body 151 in a direction towards a diametrically opposed side of the main body 151. The indentation 156 may include a depth in a direction extending perpendicular to the rotational axis of the rotor 150 penetrating from the one side surface beyond the rotational axis of the rotor 150, as desired.
The indentation 156 may have a profile having a curvilinear shape wherein a rate of change of the cross-sectional flow area through the SDD 20 as the rotor 150 is rotated relative to the stator 30 is varied at different rotational positions of the rotor 150. For example, the indentation 156 is shown in
The curvilinear shape of the profile of the indentation 156 may be selected to minimize or alter the acoustic pressure levels of the refrigerant when passing through the SDD 20. The curvilinear shape of the profile of the indentation 156 may be further selected to “tune” the SDD 20 for different acoustic pressure frequencies to control the frequency of vibrations experienced by the SDD 20, as desired. For example, it may be beneficial to tune the SDD 20 for a specific acoustic pressure frequency to avoid producing an acoustic pressure frequency similar to a resonant frequency of any portion of the HVAC system of the motor vehicle, and especially the evaporator of the HVAC system where suction pulsations are readily audible in the passenger compartment of the motor vehicle. The shape of the profile of the indentation 156 may accordingly be selected to both lower the amplitude of the acoustic pressure vibrations as well as to change the frequency at which the acoustic pressure vibrations occur.
An SDD 120 utilizing the rotor 150 operates in similar fashion to the SDD 20 having the rotor 50. The rotor 150 is rotated by the electromagnetic device 61 to a plurality of different rotational positions relative to the stator 30 to cause an overlap formed between the indentation 156 of the rotor 150 and each of the first opening 33 and the second opening 34 of the stator 30 to vary, thereby creating varying cross-sectional flow areas through the SDD 120 for passing the refrigerant. The rotational position of the rotor 150 relative to the stator 30 is similarly controlled by the controller 96 with reference to the look-up table stored to the memory of the controller 96.
From the foregoing description, one ordinarily skilled in the art can easily ascertain the essential characteristics of this invention and, without departing from the spirit and scope thereof, can make various changes and modifications to the invention to adapt it to various usages and conditions.
