Expansion valve with Anti-jamming system

Abstract

A valve includes a valve body defining a first seat surrounding an orifice, and a valve element movably disposed within the valve body. The valve element moves between a first position where it engages the first seat to close the orifice, and a second position where it disengages from the first seat to open the orifice. A nut is movably coupled within the valve body and engaged with the valve element such that relative rotation between the nut and valve element causes the valve element to move between positions. An actuator applies torque to one of the valve element and nut to rotate it relative to the other. An anti-jamming feature dissipates torque from the actuator when the valve element moves into the first position, allows torque buildup for disengagement, and absorbs energy to reduce force between components while enabling improved operation.

Description

EXPANSION VALVE WITH ANTI-JAMMING SYSTEMCROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application claims the benefit of U.S. Provisional Application No. 63 / 802,183, filed May 8, 2025, and U.S. Provisional Application No. 63 / 709,309, filed October 18, 2024, each of which is incorporated herein by reference in its entirety.BACKGROUND

[0002] The present disclosure relates to electronic expansion valves for use in refrigeration systems, and more specifically, systems and methods of operating an electronic expansion valve for regulating the flow of refrigerant through vehicles.SUMMARY

[0003] This summary is provided to introduce a selection of concepts in a simplified form that are further described below in the detailed description. This summary is not intended to identify key features or essential features of the claimed subject matter, nor is it intended to be used as an aid in determining the scope of the claimed subject matter.

[0004] According to one aspect of the present disclosure, a valve can include a valve body defining a first seat surrounding an orifice, and a valve element movably disposed within the valve body. The valve element moves between a first position where the valve element is engaged with the first seat to close the orifice, and a second position where the valve element is disengaged from the first seat to open the orifice. The valve can include a nut movably coupled within the valve body, the nut engaged with the valve element such that relative rotation between the nut and the valve element causes the valve element to move between the first position and the second position. The valve can include an actuator that applies torque to one of the valve element and the nut to rotate the one of the valve element and the nut relative to the other of the valve element and the nut. The valve can include an anti-jamming feature that dissipates torque from the actuator that applied to the one of the valve element and the nut when the valve element is moved into the first position from the second position.

[0005] In some examples, the anti -jamming feature may allow the actuator to build torque prior to the valve element disengaging the first seat when the valve element is moved towards the second position from the first position.1QB' 135236.00359\99077046.1 AU40622-40659

[0006] Tn some examples, the actuator may rotate the nut relative to the valve element, the actuator including a torsion rod that is coupled to the nut.

[0007] In some examples, the actuator may be a motor having a stator and a rotor that is rotated by the stator about an axis, the nut and the valve element being concentric with the axis such that the nut rotates about the axis and the valve element translates along the axis.

[0008] In some examples, the rotor may include an outer shell, a magnet coupled to the outer shell, and the torsion rod coupled to the outer shell by a beam, the torsion rod extending through the outer shell and allowing the outer shell to rotate relative to the nut.

[0009] In some examples, the outer shell, the beam, and the torsion rod may be formed as a unitary component.

[0010] In some examples, the nut may be secured to the valve body via a bendable tab of the valve body.

[0011] In some examples, the nut may include a flange positioned between a first bearing and a second bearing, the first bearing positioned between the bendable tab and the flange.

[0012] In some examples, the valve may further include a seal positioned between the nut and the first seat, the valve element slidably extending through the seal such that a first end of the valve element that engages the first seat is on a first side of the seal and a second end of the valve element that engages the nut is on a second side of the seal that is opposite the first side.

[0013] In some examples, the valve body may include a first valve body defining the first seat, and a second valve body coupled to the nut and the actuator, the seal secured between the first valve body and the second valve body.

[0014] In some examples, the valve element may include a channel extending through the valve element from the first end to the second end to communicate pressure at the first end of the valve element to the second end of the valve element when the valve element is in the first position.

[0015] According to another aspect of the present disclosure, an electronic expansion valve can include a valve body defining a first seat surrounding an orifice, a valve element movably disposed within the valve body, the valve element moving between a first position where the valve element is engaged with the first seat to close the orifice, and a second position where the valve element is disengaged from the first seat to open the orifice. The electronic expansion valve can include an actuator that moves the valve element between the first position and the second position, and an anti-jamming feature that absorbs energy from the actuator to allow the actuator to move2QB' 135236.00359199077046. 1 AU40622-40659relative to the valve element when the valve element is stopped in the first position, such that the anti -jamming feature reduces force applied between the valve element and the first seat when the valve element engages the first seat.

[0016] In some examples, the anti -jamming feature may allow the actuator to build momentum to increase the force applied to the valve element when the valve element disengages the first seat.

[0017] In some examples, the anti-jamming feature may be disposed in the valve body.

[0018] In some examples, the anti -jamming feature may be disposed in the actuator.

[0019] In some examples, the actuator may define a second seat and the valve element may engage the second seat in the second position, and the anti -jamming feature may absorb energy from the actuator to allow the actuator to move relative to the valve element when the valve element is stopped in the second position, such that the anti-jamming feature reduces force applied between the valve element and the second seat when the valve element engages the second seat.BRIEF DESCRIPTION OF THE DRAWINGS

[0020] The accompanying drawings, which are incorporated in and form a part of this specification, illustrate embodiments of the disclosure and, together with the description, serve to explain principles of the embodiments:

[0021] FIG. 1 is an example refrigeration system according to an example of the present disclosure.

[0022] FIG. 2 is a right side view of an electronic expansion valve for use in the refrigeration system of FIG. 1, according to an example of the present disclosure.

[0023] FIG. 3 is a cross-sectional view along III-III of the electronic expansion valve of FIG. 2.

[0024] FIG. 4 is an axonometric view of an electronic expansion valve for use in the refrigeration system of FIG. 1, according to another example of the present disclosure.

[0025] FIG. 5 is a cross-sectional view along V-V of the electronic expansion valve of FIG. 4.

[0026] FIG. 6 is a detail view of a valve body of the electronic expansion valve of FIG. 4.

[0027] FIG. 7 is a partial cross-sectional view of a rotor of the electronic expansion valve ofFIG. 4.

[0028] FIG. 8 is a top view of the rotor of the electronic expansion valve of FIG. 4.3QB' 135236.00359\99077046.1 AU40622-40659DETAILED DESCRIPTION

[0029] The following description sets forth exemplary aspects of the present disclosure. It should be recognized, however, that such description is not intended as a limitation on the scope of the present disclosure. Rather, the description also encompasses combinations and modifications to those exemplary aspects described herein.

[0030] As briefly described above, refrigeration systems generally include an electronic expansion valve to regulate flow of a refrigerant. The electronic expansion valve may be disposed between a condenser and evaporator component to modulate refrigerant flow rates in real-time based on system conditions such as evaporator temperature, pressure differentials, or electronic control signals. Expansion valves control flow by utilizing a valve element that moves between open and closed positions to regulate fluid passage through an orifice. The valve element can include a poppet that engages with a seat to provide metering capabilities. That is, the valve element can be moved away from the seat to control an effective open area of the orifice between a closed configuration corresponding with a zero open area and an open configuration corresponding with a maximum open area. An actuator, such as a motor, solenoid, or another type of actuator is configured to move the valve element between the closed configuration and the open configuration.

[0031] In conventional systems, it is possible that a valve element may become jammed or stuck in the closed position or the open position. Jamming typically occurs when the valve element impacts a valve seat with excessive force during rapid closure. The high impact forces can cause the valve element to bind against the valve seat. This binding creates a mechanical interference that inhibits subsequent movement of the valve element. In some cases, the actuator may lack sufficient torque to overcome the binding forces and reopen the valve. Jamming can also result from rotational inertia of moving components that continues after the valve element contacts the valve seat.

[0032] To prevent jamming of the valve element, an expansion valve according to the present disclosure includes an anti-jamming feature (e.g., an anti-jamming system) that can reduce or eliminate jamming of the valve element in the open configuration or the closed configuration. This is accomplished by allowing for relative movement between the valve element and the rest of the system (e.g., the actuator) to selectively reduce or increase the forces imparted to the valve element by the actuator. For example, the anti -jamming feature can include a damper or other lost motion4QB' 135236.00359199077046.1 AU40622-40659device that can allow the valve element to stop upon reaching the open configuration or the closed configuration while allowing the rest of the system to continue to decelerate so as not to impart extra force into the valve element when the valve element comes to a stop. In other cases, the antijamming feature may allow the valve element to remain stationary while allowing the rest of the system to accelerate, as may allow the system to generate inertia to start moving the valve element with greater force.

[0033] FIG. 1 illustrates an example of a refrigeration system 100, according to the present disclosure. As shown, the refrigeration system 100 includes a compressor 104 that pressurizes refrigerant vapor and delivers the pressurized vapor to a condenser 108. The condenser 108 removes heat from the refrigerant vapor to convert the refrigerant vapor to a high-pressure liquid, which flows to an evaporator 112. The evaporator 112 absorbs heat from the surrounding environment to convert the refrigerant liquid back to a vapor, which is then sent back to the compressor 104.

[0034] Flow of the refrigerant through the refrigeration system 100 can be regulated by one or more valves. For example, an expansion valve 116 (e.g., an electronic expansion valve) is positioned between the condenser 108 and the evaporator 112. The expansion valve 116 controls refrigerant flow from the condenser 108 to the evaporator 112. In particular, the electronic expansion valve 116 regulates the flow rate and pressure drop of refrigerant entering the evaporator 112, which enables the refrigeration system 100 to maintain an optimal cooling temperature during operation. In some cases, a sensor 120 monitors the temperature and pressure output of the evaporator 112 which controls this operation of the electronic expansion valve 116. For example, the sensor 120 is configured to provide feedback signals to the electronic expansion valve 116 to adjust refrigerant flow for optimal performance.

[0035] Turning now to FIGS. 2 and 3, the expansion valve 116 includes an actuator 124 and is coupled to a housing 128 or other structure of the refrigeration system 100. As shown, the manifold 128 is positioned along a passage 130 (e.g., a passage between the condenser 108 and the evaporator 112). More specifically, the manifold 128 defines the passage 130. The passage 130 extends through the manifold 128 and is fluidly coupled with the condenser 108 and the evaporator 112. Correspondingly, the expansion valve 116 can control flow of the refrigerant between a first section 132 of the passage 130 and a second section 136 of the passage 130. In this5QB' 135236.00359199077046. 1 AU40622-40659example, the first section 132 serves as the outlet for refrigerant flowing from the condenser 108 and the second section 136 serves as the inlet to the evaporator 112.

[0036] In this case, the electronic expansion valve 116 is received in an opening defined in the manifold 128 (e.g., between the first section 132 and the second section 136) to selectively block and unblock the passage 130. More specifically, the expansion valve 116 includes a valve body 142 that is coupled to the manifold 128 (e.g., within the opening thereof). The valve body 142 defines a first port 144 and a second port 146, through which the refrigerant flows. The first port 144 is a side port defined in a side of the valve body 142. The second port 146 is a nose port that is defined in a nose (e.g., a first end) of the valve body 142. The valve body 142 further defines an interior cavity 148. Within the interior cavity 148, the valve body 142 defines a first seat 152 that surrounds an orifice 156. The first seat 152 is positioned between the first port 144 and the second port 146. This positioning allows fluid to flow through the orifice 156 between the first port 144 and the second port 146. Accordingly, the refrigerant flows along the passage 130 as it flows between the first port 144 and the second port 146 through the orifice 156. In other example, the orifice 156 or the first seat 152 can be provided differently.

[0037] To control flow, the expansion valve 116 includes a valve element 158 that is movable relative to the first seat 152 to open and close the orifice 156. In operation, the first seat 152 provides a sealing surface which the valve element 158 selectively engages to control fluid flow during operations. For example, in a closed configuration, the valve element 158 engages the first seat 152 (e.g., in a first position of the valve element 158) to block a flow 160 through the passage 130. In an open configuration, the valve element 158 is moved away from the first seat 152 (e.g., in a second position of the valve element 158) to open the orifice 156 and allow the flow 160 through passage 130. As the valve element 158 moves from the open configuration to the closed configuration, the first seat 152 can function as a stop that prevents further movement of the valve element 158. Similarly, and as described in greater detail below, the expansion valve 116 can include a second seat (e.g., end stop 162) that prevents further movement of the valve element 158 moves from the closed configuration to the open configuration.

[0038] In the illustrated example, the valve element 158 is configured as a pin; however, other types of valve element can also be used. The valve element 158 includes a tapered or conical end that engages with the first seat 152. Correspondingly, the first seat 152 has a conical or tapered6QB' 135236.00359\99077046.1 AU40622-40659geometry that matches a corresponding shape of the valve element 158 to achieve effective sealing and minimize leakage when the valve element 158 moves to the closed position.

[0039] To move the valve element 158 between the closed configuration and the open configuration, the expansion valve 116 further includes the actuator 124. The actuator 124 is coupled to an end (e.g., a second end) of the valve body 142 that is opposite the nose. The actuator 124 moves the valve element 158 to move between the open configuration and the closed configuration. More specifically, the actuator 124 can be rotated along a rotational axis RA which causes the valve element 158 to move between the open configuration and the closed configuration along the rotational axis RA.

[0040] For example, the actuator 124 may be operated by a controller that provides control signals to regulate the position of the valve element 158. The controller can be a controller of the expansion valve 116, a controller of the refrigeration system 100, or another controller configured to manage valve operations. In some cases, the controller receives input signals from sensors, such as sensor 120, that monitor system conditions including temperature, pressure, or flow rates. Based on these input signals, the controller may generate appropriate control commands to position the valve element 158 at a desired location between the fully closed and fully open configurations. The controller may operate the actuator 124 to provide precise positioning control of the valve element 158. For example, when cooling demand increases, the controller can command the actuator 124 to move the valve element 158 away from the first seat 152 to increase refrigerant flow through the orifice 156. Conversely, when cooling demand decreases, the controller may command the actuator 124 to move the valve element 158 toward the first seat 152 to reduce refrigerant flow. This controlled positioning allows the expansion valve 116 to modulate refrigerant flow rates based on system operating conditions.

[0041] In this example, the actuator 124 is configured as a motor, and more particularly, a stepper motor that enables precise positional control of the valve 116 and repeatable positioning accuracy for flow metering applications, although other configurations are possible. Correspondingly, the actuator 124 may rotate the valve element 158. The rotation of the valve element 158 can be converted into linear displacement of the valve element 158, as described in greater detail below, which moves the valve element 158 between the open configuration and the closed configuration.7QB' 135236.00359199077046. 1 AU40622-40659

[0042] The valve element 158 may be coupled to the actuator 124 through a coupling arrangement that allows rotational engagement while permitting axial movement. In some aspects, the valve element 158 includes an anti-rotation feature, such as a flat or keyed portion, a spline that engages with a corresponding feature in a rotor 166 or drive component of the actuator 124. This engagement prevents relative rotation between the valve element 158 and the rotor 166 while allowing the valve element 158 to translate axially along its rotation axis. In some cases, the valve element 158 extends through an opening 168 in the rotor 166 that has a complementary noncircular shape. This configuration allows the valve element 158 to slide axially through the rotor opening 168 while being rotationally coupled to move with the rotor 166 (e.g., relative to the rotational axis RA of the rotor 166).

[0043] To help support the valve element 158 during movement, a guide 170 (e.g., a guide bearing) is positioned within the interior cavity 148 of the valve body 142. In this example, the guide 170 maintains alignment of the valve element 158 during operation. The guide 170 defines an opening that allows the valve element 158 to extend through the guide 170. This opening permits the valve element 158 to couple with the actuator 124 while maintaining proper alignment within the interior cavity 148. In this example, the guide 170 is also configured to utilize low- friction bearing materials that reduce friction and wear of the valve element 158 while preventing lateral displacement of the valve element 158 during axial movement. The guide 170 can close the interior cavity 148 on the second end of the valve body 142.

[0044] Referring still to FIG. 3, the electronic expansion valve 116 further includes the end stop 162, opposite the first seat 152. The end stop 162 can prevent further movement of the valve element 158 when the valve element 158 reaches the open configuration. That is, the end stop 162 acts as a second stop that the valve element 158 engages when maximum flow conditions are achieved through the valve orifice 156 in the open configuration. In the illustrated example, the end stop 162 is defined by the actuator 124. More specifically, the actuator 124 includes a rotor tube 172 that surrounds the rotor 166. The rotor tube 172 is positioned between a gap between the rotor 166 and a stator 174 of the actuator 124. The dual seat arrangement of the first 152 and second seat 162 allow the electronic expansion valve 116 to provide controlled positioning of the valve element 158 at both extremes of the operational range, ensuring predictable valve 116 behavior during both fully-closed and fully-open operating conditions.8QB' 135236.00359199077046. 1 AU40622-40659

[0045] To convert rotational motion from the actuator 124 into linear displacement of the valve element 158, the electronic expansion valve 116 also includes a threaded connection between the valve element 158 and a nut 176. The nut 176 is moveably received in the interior cavity 148 of the valve body 142. More specifically, the nut 176 is disposed between the first seat 152 and the guide 170 within the interior cavity 148. The nut 176 is positioned coaxial with the rotational axis RA of the actuator 124. The nut 176 is rotationally locked with the valve body 142 such that the nut 176 does not rotate relative to the valve body 142. The nut 176 can move linearly along the same direction as the valve element 158, which can allow the nut 176 to act as an anti-jamming feature, as described in greater detail below. This linear movement occurs along the motor axis of the actuator 124.

[0046] The nut 176 includes a first thread (e.g., an internal thread) that engages with a second thread (e.g., an external thread) of valve element 158. The threaded interface between the nut 176 and the valve element 158 may use a fine pitch to provide enhanced linear positioning resolution and mechanical advantage for accurate flow control and precise flow metering. In some examples, the threading pitch is selected based on desired flow control resolutions and a step angle of the stepper motor actuator 124. The thread of the can also be configured to reduce backlash.

[0047] When the actuator 124 rotates the valve element 158, the threaded engagement between the valve element 158 and the nut 176 converts this rotational motion into linear translation along the rotational axis RA. The valve element 158 rotates within the stationary nut 176, causing the valve element 158 to advance or retract along the threaded interface depending on the direction of rotation. For example, the valve element 158 can be rotated in a first direction of rotation (e.g., a clockwise rotation) to cause the valve element 158 to translate toward the first seat 152, moving the valve element 158 from the open configuration to the closed configuration. Conversely, the valve element 158 can be rotated in a second direction of rotation (e.g., anticlockwise rotation) to cause the valve element 158 to translate away from the first seat 152, moving the valve element 158 from the closed configuration toward the open configuration. During rotation of the valve element 158, the nut 176 remains stationary relative to the valve body 142. This arrangement allows the rotating valve element 158 to thread through the nut 176 while the nut 176 provides a stable reference point for the linear translation.

[0048] As mentioned above, the nut 176 is translatable in the direction of movement of the valve element 158. The movement of the nut 176 allows the nut 176 to translate relative to the9QB' 135236.00359\99077046.1 AU40622-40659valve element 158 when the valve element 158 engages the first seat 152 or the end stop 162, but continues to rotate. In this way, the nut 176 is translated rather than the valve element 158 to reduce or prevent jamming of the valve element 158. By preventing jamming, locking forces that would otherwise retain the valve element 158 and have to be overcome by the actuator 124 can be reduced. This allows for a smaller actuator to be used, which in turn consumes less energy.

[0049] During operation, the nut 176 moves in a direction opposite that of the valve element 158. For example, when the valve element 158 is rotated in the first direction to move to the closed configuration and engage the first seat 152, the valve element 158 stops moving axially upon contact with the first seat 152. However, the actuator 124 may continue rotating the valve element 158 due to rotational inertia. This continued rotation causes the nut 176 to move axially in a direction opposite to the valve element's 140 previous movement direction, in this case, away from the first seat 152. Similarly, when the valve element 158 is rotated in the second direction to move to the open configuration and engage the end stop 162, the valve element 158 stops moving axially upon contact with the end stop 162. However, the actuator 124 may continue rotating the valve element 158 due to rotational inertia. This continued rotation causes the nut 176 to move axially in a direction opposite to the valve element's 140 previous movement direction, in this case, toward the first seat 152. Movement of the nut 176 can be limited by the valve body 142 (e.g., the first seat 152) or the guide 170.

[0050] In some cases, one or more resilient members can be used to dissipate kinetic energy of the nut 176, such as to absorb impact forces when the valve element 158 reaches the open configuration or the closed configuration. Still referring to FIG. 3, the expansion valve 116 includes a first resilient member 180. The first resilient member 180 is positioned at a first end of the nut 176 between the nut 176 and the guide 170. In this way the first resilient member 180 can absorb and dissipate energy when valve element 158 is moved to the closed configuration. During operation, when the valve element 158 moves to the closed configuration and contacts the first seat 152, which causes the nut 176 moves away from the first seat 152, the first resilient member 180 becomes compressed between the nut 176 and the guide 170. The compression of the first resilient member 180 creates a reaction force that opposes further movement of the nut 176. The reaction force dissipates the excess motion of the system in a controlled manner that allows for gradual deceleration of the nut 176 rather than abrupt stop that can generate high impact forces. The first resilient member 180 continues to compress until the torque generated by the compressed10QB' 135236.00359\99077046.1 AU40622-40659first resilient member 180 balances the rotational forces in the valve 116. In this way the first resilient member 180 can absorb and dissipate energy when valve element 158 is moved to the closed configuration. This reduces the forces between the first seat 152 and the valve element 158 to prevent lock-up of the valve element 158.

[0051] The expansion valve 116 may further include a second resilient member 182. The second resilient member 182 is positioned at a second end of the nut 176 between the nut 176 and the valve body 142 (e.g., the first seat 152). In this way the first resilient member 180 can absorb and dissipate energy when valve element 158 is moved to the open configuration. During operation, when the valve element 158 moves to the open configuration and contacts the end stop 162, the valve element 158 stops moving axially. Continued rotation of the valve element 158 causes the nut 176 to move toward the first seat 152. This movement compresses the second resilient member 182 between the nut 176 and the valve body 142. The compression of the second resilient member 182 creates a reaction force that opposes further movement of the nut 176. The reaction force dissipates the excess motion of the system in a controlled manner that allows for gradual deceleration of the nut 176 rather than abrupt stop that can generate high impact forces. The second resilient member 182 continues to compress until the torque generated by the compressed second resilient member 182 balances the rotational forces in the valve 116. In this way the second resilient member 182 can absorb and dissipate energy when valve element 158 is moved to the open configuration. This reduces the forces between the end stop 162 and the valve element 158 to prevent lock-up of the valve element 158.

[0052] In some cases, the first resilient member 180 and the second resilient member 182 may be configured as O-rings. For example, the O-rings provide compressive sealing and energy absorption capabilities. In other examples, the first resilient member 180 and the second resilient member 182 may be formed from elastomeric materials such as nitrile rubber, fluorocarbon rubber, or silicone rubber. These materials exhibit suitable compression characteristics under the operating conditions of the expansion valve 116. The elastomeric material of the first resilient member 180 and the second resilient member 182 allows the first resilient member 180 and the second resilient member 182 to compress and expand repeatedly without permanent deformation. This characteristic enables the first resilient member 180 and the second resilient member 182 to absorb kinetic energy from the moving nut 176. The first resilient member 180 and the second resilient member 182 return to their original shape when the compressive forces are removed. The11QB' 135236.00359\99077046.1 AU40622-40659material selection may also consider chemical compatibility with the refrigerant and other fluids in the system to prevent degradation over time.

[0053] In some cases, the nut 176 may include chamfers at each end of the nut 176. The chamfers facilitate proper positioning and retention of the first resilient member 180 and the second resilient member 182. The chamfers provide angled surfaces that guide the first resilient member 180 and the second resilient member 182 into position during assembly. The chamfers help maintain alignment of the first resilient member 180 and the second resilient member 182 during operation. The chamfered surfaces may also reduce stress concentrations on the first resilient member 180 and the second resilient member 182.

[0054] FIG. 4 is an example electronic expansion valve 216 for use in the refrigeration system 100 according to another aspect of the present disclosure. In this example, the electronic expansion valve 216 is similar to the electronic expansion valve 116 of FIGS. 1-3, with similar features labeled with similar reference numerals increased by 100, unless specified otherwise. In particular, the electronic expansion valve 216 has an actuator 224, a manifold 128, a passage 230 having a first section 232 and a second section 236, and a valve body 242. In this case, the valve body 242 is configured as a two-piece valve body (e.g., configured as a first valve body 242a, and a second valve body 242b) coupled to one another. The two-piece construction may allow for easier machining of internal features such as valve seats, bearing surfaces, and threaded portions by providing access from multiple directions during manufacturing operations. This configuration may also facilitate assembly of internal components by allowing the valve body sections 242a, 242b to be separated during the assembly process before being joined together. The two valve body pieces 242a, 242b may be coupled through various methods such as threaded connections, press-fit interfaces, welding, or mechanical fasteners, with the joining method selected based on the pressure requirements and sealing needs of the valve application. The two-piece design may also enable the use of different materials for each section to optimize performance characteristics, such as using harder materials for seating surfaces while employing more machinable materials for housing components. In some cases, the two-piece construction may simplify maintenance and repair operations by allowing disassembly of the valve body pieces 242a, 242b for access to internal components when service is required.

[0055] In this example, the first section 232 of the first valve body 242a defines a first port244 that is fluidly connected to and serves as an outlet for refrigerant from the condenser 108.12QB' 135236.00359199077046. 1 AU40622-40659Correspondingly, the second section 236 of the first valve body 242a defines a second port 246 that is fluidly connected to and serves as an inlet to the evaporator 112 of the system 100. Accordingly, fluid flows from the condenser 108, through the first port 244 of the first section 232, out the second port 246 of the second section 236, and to the evaporator 112. Furthermore, in this example, the first port 244 is a side port defined in a side of the first valve body 242a. The second port 246 is configured as a nose port that is defined in a nose 247 (e.g., a first end) of the first valve body 242a.

[0056] With particular reference to FIG. 5, the first valve body 242a and the second valve body 242b define an interior cavity 248, and the first valve body 242a defines a first seat 252 that is positioned between the first port 244 and second port 246 and surrounds an orifice 256. In this example, the orifice 256 is formed as the second port 246, and so, corresponding discussion of the orifice 256 similarly applies to the second port 246. Accordingly, flow control through the orifice 256 and the second port 246 are integrated into a single feature rather than being separate components. This configuration simplifies the valve body 242 design by eliminating the need for additional machining operations or separate orifice components, reducing manufacturing complexity and potential leak paths. In this way, the second port 246 serves the dual function of providing the outlet connection for fluid flow while also defining the orifice geometry that works in conjunction with a valve element 258 to control flow rates.

[0057] Continuing, the valve element 258 is movable within the interior cavity 248 of the second valve body 242b relative to the first seat 252 to open and close the orifice 256, providing control of fluid flow through the valve 216. In particular, when the valve element 258 moves away from the first seat 252, an increase in flow area is created between the tapered surfaces of the valve element 258, allowing fluid to pass from the inlet and exit through the orifice 256. As the valve element 258 approaches the first seat 252, the flow area progressively decreases, reducing the flow rate through the orifice 256 until the valve element 258 fully contacts the first seat 252 to completely block the fluid passage 230. In this way, the first seat 252 provides a sealing surface which the valve element 258 selectively engages to control fluid flow during operations.

[0058] As similarly discussed above, the first seat 252 and a second end stop 262 acts as stops that prevent further movement of the valve element 258 as the valve element 258 moves from the open configuration to the closed configuration, and vice versa, respectively, and will be further detailed below. In this example, the valve element 258 extends through the orifice 256 during13QB' 135236.00359\99077046.1 AU40622-40659axial movement while remaining positioned within the manifold 128 so that it does not protrude beyond the external surfaces of the manifold 128. Accordingly, the valve element 258 stays protected within the valve body 242 throughout its operational range while providing effective flow control through modulation of the orifice 256 based on its position relative to the first seat 252.

[0059] In this example, the valve element 258 is configured as a poppet. Furthermore, the valve element 258 is rotationally fixed. For example, the valve element 258 is prevented from rotating by an anti-rotation feature 263 of the valve element 258 which engages with a corresponding feature of the first valve body 242a. In particular, the anti-rotation feature 263 creates a mechanical interface that constrains rotational movement of the valve element 258 while allowing axial movement during valve operation. In this example, the anti-rotation feature 263 is configured as a flat that is machined along a portion of the poppet surface and positioned to engage with an anti -rotation pin 264 or projection within the first valve body 242a when the valve element 258 approaches the closed position. In other examples, the anti-rotation feature 263 may alternatively be configured as a key, spline, hexagonal section, or other non-circular geometry that provides rotational constraint while permitting axial translation. The engagement between the anti-rotation feature 263 and the pin 264 prevents unwanted rotation of the valve element 258 and maintains proper alignment between the valve element 258 and the first seat 252 throughout the operational stroke. The engagement further improves sealing performance and preventing binding or misalignment that could affect valve operation. The anti-rotation feature 263 and corresponding valve element 258 may be designed with appropriate clearances to allow smooth axial movement of the valve element 258 while providing rotational constraint.

[0060] To move the valve element 258 between the closed configuration and the open configuration, the valve 216 further includes the actuator 224 coupled to an end of the second valve body 242b (e.g., a second end) opposite the nose 247. In particular, the actuator 224 can be actuated to cause the valve element 258 to move between the closed configuration and the open configuration, as noted above. In some cases, the actuator 224 may be operated by a controller, which may receive signals from sensors monitoring system conditions such as temperature, pressure, or flow rates, and generates control commands to position the valve element 258 at desired locations between fully closed and fully open configurations. The controlled positioning of the valve element 258 allows the expansion valve 216 to modulate refrigerant flow rates based14QB' 135236.00359\99077046.1 AU40622-40659on system operating conditions. The controller commands the actuator 224 to move the valve element 258 away from or toward the first seat 252 to increase or decrease refrigerant flow in response to changing cooling demands. This operation is similar to that discussed above.

[0061] In this example, the actuator 224 is configured as a stepper motor that enables precise positional control and repeatable positioning accuracy for flow metering applications, with rotation converted into linear displacement that moves the valve element 258 between the open and closed configurations through threaded engagement. In the illustrated example, the actuator 224 includes a rotor tube 272 that surrounds the rotor 266. The rotor tube 272 is positioned between a gap between the rotor 266 and a stator 274 of the actuator 224.

[0062] To convert rotational motion from the actuator 224 into linear displacement of the valve element 258, the electronic expansion valve 216 includes a threaded connection between the valve element 258 and a nut 276. The nut 276 is rotatably received in the interior cavity 248 of the second valve body 242b and is positioned coaxial with a rotational axis RA of the actuator 224. In particular, the nut 276 receives rotational torque from the actuator 224 while the valve element 258 is rotationally locked with the valve body 242 such that the valve element 258 does not rotate relative to the valve body 242. The threaded engagement between the rotating nut 276 and the rotationally-stationary valve element 258 converts the rotational motion into linear displacement of the valve element 258 along the rotational axis RA of the actuator 224. Here, the nut 276 includes an internal thread that engages with an external thread of the valve element 258. The threading pitch may be selected based on the step angle of the stepper motor actuator 224, and can be configured to reduce backlash in the system.

[0063] When the actuator 224 rotates the nut 276, the threaded engagement between the rotating nut 276 and the stationary valve element 258 converts this rotational motion into linear translation of the valve element 258. The valve element 258 can translate toward the first seat 252 to move from the open configuration to the closed configuration, or translate away from the first seat 252 to move from the closed configuration toward the open configuration, depending on the direction of nut rotation. During rotation of the nut 276, the valve element 258 remains rotationally locked relative to the valve body 242, allowing the rotating nut 276 to thread along the stationary valve element 258 while providing controlled linear displacement.

[0064] In this example, the nut 276 includes a flange 278 that extends radially outward from the main body of the nut 276. The flange 278 is positioned between bearing elements that support15QB' 135236.00359199077046. 1 AU40622-40659the nut 276 and allow the nut 276 to rotate with minimal friction during valve operation. In particular, bearing elements include a first set of bearing elements 280 positioned above the nut flange 278 (e.g., relative to the second end stop 262) and a second set of bearing elements 282 positioned below the nut flange 278, creating a captured bearing system where the nut flange 278 remains positioned between the two sets of bearing elements 280, 282 throughout the operational range. This dual bearing arrangement provides bidirectional thrust load support as the valve element 258 axially translates along the valve body 242, allowing the nut 276 to react thrust forces regardless of the direction of valve element 258 movement and distributing the axial loads across multiple contact points to reduce contact stress on individual bearing elements. Accordingly, the thickness and diameter of the nut flange 278 are configured based on the thrust loads that the bearing system experiences during valve operation. In this example, the nut flange 278 is machined as an integral part of the nut 276, eliminating the need for separate thrust bearing components and reducing overall assembly complexity, although other configurations are possible.

[0065] The bearing elements 280, 282 may comprise roller balls or other rolling elements that provide point or line contact interfaces between the rotating nut 276 and the stationary valve body components, significantly reducing friction forces compared to sliding bearing arrangements while extending the operational life of the bearing system. During operation, the thrust forces produced on the nut 276 are reacted directly to the valve body 242 through the first 280 and second bearing elements 282. In this way, the backlash of the mechanism is minimized because there are fewer feature tolerances that combine in the load path, and the first 280 and the second bearing elements 282 maintain consistent positioning compared to sliding interfaces that may exhibit greater clearance variations due to wear or manufacturing tolerances.

[0066] Turning briefly to FIG. 6, the first set of bearing elements 280 is disposed between a top washer 308 and the flange 278 while the second bearing elements 282 is positioned between the nut flange 278 and the valve body 242. As further shown in FIG. 6, the top washer 308 is engaged with the first set of bearing elements 280 to provide a stable bearing raceway that supports the thrust loads generated during valve 216 operation while maintaining proper positioning of the bearing elements 280, 282 within the valve 216. In this way, the top washer 308 serves as an upper bearing surface that reacts the axial forces transmitted through the first set of bearing elements 280 from the nut flange 278, distributing these loads across the washer 308 surface to prevent excessive contact stresses that could cause premature wear or deformation of the bearing elements 280, 282.16QB' 135236.00359199077046. 1 AU40622-40659In this example, the top washer 308 is constructed from hardened steel or other bearing-grade materials that provide smooth, wear-resistant contact surfaces for the first 280 and second bearing elements 282, although other configurations are possible.

[0067] Continuing, the top washer 308 is retained by a tab 312 that provides a permanent mechanical retention of the top washer 208. In particular, the bent tab 312 is formed by deforming a corner of the second valve body 242b to displace material into a bore that receives the washer 308 to trap the washer 308 into place by creating a shoulder or lip feature that bears against the washer 308 surface to prevent movement in the axial direction.

[0068] To provide sealing for the valve element 258, a seal 284 is disposed within a corresponding recess 286 within the second valve body 242b. As shown in FIG. 5, the seal 284 is positioned between the first valve body 242a and the second valve body 242b. The seal 284 engages the valve element 258 to prevent fluid leakage during operation across varying pressure and temperature conditions encountered during operation. As shown, the seal 284 has an inner diameter 285 and an outer diameter 287, which are both larger than a diameter than the first seat 252. In particular, the inner diameter 285 defines an aperture 289 through which the valve element 258 extends through. In this example, a hollow interior 291 (e.g., a channel) of the valve element 258 communicates pressure experienced on the valve element 258 at the first end 247 and the second end adjacent the second end stop 262. The seal 284 enables this pressure of the valve element 258 to be balanced by preventing fluid to flow past the seal 284 that would otherwise flow through the valve element 258 and out of the orifice 256 or within the interior cavity 248 defined by the second valve body 242b. Accordingly, the hollow interior 291 creates a pressure-balanced condition that reduces the net force required to move the valve element 258 against system pressure and enables the use of smaller actuators with reduced electrical power consumption. This pressure balancing effect enables system pressure that acts on equal and opposite areas of the valve element 258, to effectively neutralize the forces that would otherwise resist valve 258 movement and significantly reducing the torque requirements for the actuator 224. The seal 284 may be made of materials such as Teflon that provide low-friction sealing contact with the moving poppet surface while maintaining effective fluid containment, with the material selection based on chemical compatibility with refrigerants and other system fluids, dimensional stability across temperature ranges, and wear resistance under sliding contact conditions, although other configurations are possible.17QB' 135236.00359199077046. 1 AU40622-40659

[0069] To maintain sealing contact between the seal 284 and the valve element 258, a resilient member 288 is disposed within the recess 286 and is positioned between the seal 284 and the second valve body 242b. In this example, the resilient member 288 biases the seal 284 into engagement with the valve element 258. The resilient member 288 comprises an O-ring or other elastomeric element that provides a consistent biasing force to compensate for wear, thermal expansion effects, and manufacturing variations that could affect sealing performance over time. This biasing arrangement ensures that the sealing contact pressure remains within the optimal range for both sealing effectiveness and low friction operation throughout the service life of the valve 216, although other configurations are possible. In other examples, other types of seal arrangements can be used, such as spring seals.

[0070] In this example, the resilient member 288 and the seal 284 are positioned on a washer 292. As shown, the washer 292 is received within a corresponding recess 294 within the first valve body 242a. In this example, the first recess 286 of the second valve body 242b and the second recess 294 of the first valve body 242a are positioned adjacent to one another. In this way, the washer 292 provides support and proper positioning for the resilient member 288 and the seal 284 within the second valve body 242b. In particular, the washer 292 serves as a stable platform that maintains proper alignment of the sealing elements throughout the operational stroke of the valve element 258. This prevents lateral displacement or distortion of the sealing components (e.g., the seal 284 and the resilient member 288) that could compromise sealing effectiveness. The washer 292 may be made from materials such as stainless steel or other corrosion-resistant alloys. These materials provide adequate strength and dimensional stability to support the sealing system loads. The materials also resist degradation from exposure to system fluids and temperature variations, although other configurations are possible.

[0071] Referring still to FIG. 5, an armature 296 is coupled to the nut 268 and includes the rotor 266. In this example, the rotor 266 has a magnet 300. In particular, an outer shell 320 (see FIG. 7) of the rotor 266 engages the magnet 300, which is coupled to the outer shell 320. In some cases, the magnet 300 is permanently coupled to the outer shell 320. For example, the outer shell 320 is injection molded over the magnet 300 to engage and encapsulate the magnet 300. In this example, the injection material is a thermoplastic material, however alternative materials such as thermoplastic elastomers, polyurethane, or other moldable polymeric compounds may be used, although other configurations are possible. The injection molding process creates a mechanical18QB' 135236.00359\99077046.1 AU40622-40659bond between the plastic material and the magnet 300, forming a unified structure that eliminates the need for separate fastening or bonding operations while providing the torsional flexibility required for anti-jamming functionality.

[0072] The outer shell 320 may incorporate features such as ribs, bosses, or other structural elements that enhance the mechanical integrity of the rotor assembly while maintaining the desired magnetic air gap between the rotor 266 and the stator 274 of the actuator 224. The electromagnetic element of the magnet 300 serves as the primary electromagnetic element of the rotor 266. In particular, the magnet 300 has multiple north and south poles arranged around the circumference of the rotor 266 to interact with electromagnetic fields from the stator 274 windings to generate rotational motion necessary for operation, with the pole arrangement configured to provide the desired step angle resolution for precise valve positioning control.

[0073] The system can further include an anti-jamming system or feature. For example, a torsion rod 304 connects the outer shell 320 to the nut 268 (see FIG. 7). The torsion rod 304 provides torsional flexibility and allows controlled angular displacement between the rotor 266 and the valve element 258 during operation, creating a compliant coupling system that manages rotational energy transfer between the motor 224 and valve element 258. In particular, a beam 324 connects the outer shell 320 to the torsion rod 304, creating the mechanical linkage that transmits rotational motion from the rotor 266 to the torsion rod 304. The torsion rod 304 is configured to couple to the nut 268 and transmits rotation of the rotor 266 to the nut 268 to cause the valve element 258 to translate.

[0074] The torsion rod 304 is configured to absorb excess rotational energy and prevent jamming by allowing the armature 296 to rotate relative to the nut 268 when high resistance forces are encountered. This controlled energy transfer and dissipation through the torsion rod 304 reduces loads from being transmitted to the first seat 252 or the second end stop 262 during operation, eliminating or reducing jamming. Correspondingly, the torsion rod 304 enables the actuator 224 to build up torque gradually before opening or closing the valve 216. This gradual torque buildup allows the actuator 224 to overcome friction and other binding forces that may develop when the valve element 258 has been stationary for extended periods.

[0075] The torsion rod 304 may be manufactured from materials that exhibit predictable elastic properties across the operational temperature range, such as spring steel or other metallic alloys that maintain their torsional characteristics under repetitive loading conditions, although19QB' 135236.00359\99077046.1 AU40622-40659other configurations are possible. The torsional flexibility characteristics of the rod 304 may allow controlled angular displacement of several degrees between the armature 296 and nut 268, enabling the actuator 224 to respond to jamming conditions to overcome binding or sticking conditions that could occur due to contamination, wear, or thermal effects. In some aspects, several degrees of controlled angular displacement may be between about zero degrees and about five degrees, or between about one degree and about ten degrees, or between about two degrees and about four degrees.

[0076] During use, when the valve element 258 contacts the first seat 252, the valve element 258 and the nut 276 come to a stop while the rotor 266 continues rotating due to rotational inertia, creating conditions that could potentially cause valve 216 jamming in conventional rigid coupling designs. In conventional designs, the inertia of the rotor 266 creates a high torque during deceleration which may jam the valve 216 so the valve 216 cannot be re-opened with the available motor torque, resulting in valve lockup that compromises system operation and may require manual intervention or higher-capacity actuators to restore functionality.

[0077] In this example, the rotor 266 is configured to provide torsional compliance between the rotor 266 and the nut 276 to allow the rotor 266 to decelerate slowly and thus prevent high inertia torque from being transmitted directly to the first seat 252 during a closing operation. Accordingly, the torsion rod 304 exhibits elastic deformation that allows angular displacement between the rotor 266 and the driven components (e g., valve element 258, nut 276), effectively decoupling the rotational inertia of the motor 224 from the mechanical resistance encountered when the valve element 258 contacts the first seat 252. In this way, the torsion rod 304 and the nut 276 acts as a torsional spring that absorbs the rotational energy over an angular displacement, dissipating the kinetic energy gradually rather than through abrupt impact forces that could wedge the valve element 258 against the first seat 252 with forces exceeding the motor's 224 reopening capability.

[0078] This torsional flexibility also allows the motor actuator 224 to ramp up speed and build torque prior to opening, which also overcomes jamming, binding, or sticking conditions that might develop while the valve 216 remains in the closed position due to thermal effects, contamination, or slight deformation of the seating surfaces under pressure. The compliant coupling enables the motor 224 to accelerate and generate higher torque levels before the full mechanical load of the valve system engages, providing additional force and momentum to break the contact between the20QB' 135236.00359\99077046.1 AU40622-40659valve element 258 and the first seat 252. For example, the motor actuator 224 is configured to rotate in a range of about 1 -degree to 10-degrees before the valve 216 opening begins, providing sufficient angular displacement to generate the additional torque needed to initiate valve 216 opening, although other rotational ranges are possible.

[0079] Conversely, when the valve element 258 moves to the fully opened position, additional anti -jamming protection may be provided through the interaction between the valve element 258 and the nut 276 as the valve element 258 becomes fully received within the threaded portion of the nut 276. In this fully open configuration, the valve element 258 may contact internal features of the nut 276 or reach the end of the threaded engagement (e.g., configured as the second end stop 262 opposite the first seat 252), creating a mechanical stop that limits further axial movement of the valve element 258 in the opening direction. Similar to the closing operation, if the motor actuator 224 continues rotating due to inertia after the valve element 258 reaches this fully open position, the torsional compliance provided by the torsion rod 304 plastic coupling system allows the rotor 266 to continue rotating while the valve element 258 remains stationary against the mechanical stop. This controlled angular displacement absorbs the excess rotational energy and prevents high impact forces that could cause binding or damage to the threaded interface or internal nut features. The energy dissipation mechanism operates bidirectionally, ensuring that the valve element 258 remains operable and can be repositioned from the fully open position without requiring excessive torque to overcome j amming conditions that might otherwise develop from abrupt stopping of the rotating components.

[0080] As mentioned above and turning now to FIG. 6, the nut 276 can couple to the rotor 266 (e.g., via the torsion rod 304). Correspondingly, the nut 276 includes a first connector that is configured to connect with a second connector of the torsion rod 304. Here, the nut 276 includes a connector with one or more protrusions 316a, 316b that extend axially outward from the nut 276. In the illustrated example, the protrusions 316a, 316b are positioned diametrically opposite each other around the circumference of the nut 276. The protrusions 316a, 316b are formed as integral features of the nut 276. In other aspects, the protrusions 316a, 316b may be added as separate components through mechanical fastening, welding, or press-fit assembly methods that allow for different material selections or manufacturing processes, although other configurations are possible. The protrusions 316a, 316b may incorporate specific geometric features such as rounded or chamfered edges that reduce stress concentrations and facilitate smooth engagement with the21QB' 135236.00359199077046. 1 AU40622-40659corresponding features of the torsion rod 304. The clearances or chamfered features facilitate smooth relative motion between the torsion rod 304 and the protrusions 316a, 316b during torsional deflection during operation.

[0081] Continuing, the protrusions 316a, 316b create mechanical engagement for torque transmission within the valve 216, serving as an interface between the rotational input from the actuator 224 and the nut 276 that converts rotary motion into linear valve element 258 displacement. The height, width, and angular positioning of the protrusions 316 are coordinated with the torsion rod 304 design to ensure proper engagement throughout the range of angular displacement that the compliant coupling system may experience during normal and abnormal operating conditions. In some aspects, alternative interface configurations may be employed, such as splined connections, keyed interfaces, pin-and-slot arrangements, or hexagonal coupling geometries that provide similar torque transmission capabilities while accommodating the torsional flexibility requirements of the anti -j mming system.

[0082] Turning now to FIG. 8, to engage the rotor 266 with the nut 276, notches 332 of the torsion bar 304 engage the protrusions 316 on the nut 276 to create a mechanical connection that transmits rotational motion while accommodating torsional flexibility required for anti -jamming operation. The notches 332 serve as female engagement features that receive the protrusions 316, creating a positive mechanical interface that prevents relative rotation under normal operating conditions while allowing controlled angular displacement when the coupling system encounters high resistance forces. In this example, the notches 332 are formed in the plastic material of the torsion rod 304 during the injection molding process to achieve precise dimensional control and consistent engagement characteristics, however in other examples the notches 332 are machined or cut into the rod 304 after molding to provide alternative manufacturing flexibility or tighter tolerance control.

[0083] The notch 332 geometry, depth, width, and angular spacing, are configured to be designed to provide adequate contact area for torque transmission while allowing the controlled angular displacement that provides the anti -jamming functionality, with the dimensions selected based on the torque requirements of the valve 216 and the desired angular displacement range of the compliant coupling. The notch 332 depth may be sufficient to fully engage the protrusions 316 under normal operating conditions while providing clearance for relative motion when the22QB' 135236.00359199077046. 1 AU40622-40659torsional coupling deflects, and the angular spacing between multiple notches 332 ensures uniform load distribution around the circumference of the coupling interface.

[0084] Correspondingly, the protrusion 316a, 316b geometry complements the notch 332 configuration to provide positive engagement that prevents slippage under normal operating torque levels while accommodating the angular displacement capabilities of the torsional coupling system. The engagement between the notches 332 and protrusions 316a, 316b are configured to incorporate clearances or chamfered surfaces that facilitate smooth engagement and disengagement as the torsional coupling flexes during operation, allowing relative motion when the coupling deflects under high load conditions while maintaining reliable torque transmission during normal valve positioning and preventing binding or excessive wear of the engagement surfaces.

[0085] In some implementations, devices or systems disclosed herein can be utilized, manufactured, or installed using methods embodying aspects of the invention. Correspondingly, any description herein of particular features, capabilities, or intended purposes of a device or system is generally intended to include disclosure of a method of using such devices for the intended purposes, a method of otherwise implementing such capabilities, a method of manufacturing relevant components of such a device or system (or the device or system as a whole), and a method of installing disclosed (or otherwise known) components to support such purposes or capabilities. Similarly, unless otherwise indicated or limited, discussion herein of any method of manufacturing or using for a particular device or system, including installing the device or system, is intended to inherently include disclosure, as embodiments of the invention, of the utilized features and implemented capabilities of such device or system.

[0086] The above discussion is presented to enable a person skilled in the art to make and use embodiments of the invention. Various modifications to the illustrated embodiments will be readily apparent to those skilled in the art, and the generic principles herein can be applied to other embodiments and applications without departing from embodiments of the invention. Thus, embodiments of the invention are not intended to be limited to embodiments shown, but are to be accorded the widest scope consistent with the principles and features disclosed herein. The above detailed description is to be read with reference to the figures in which like elements in different figures have like reference numerals. The figures, which are not necessarily to scale, depict selected embodiments and are not intended to limit the scope of embodiments of the invention.23QB' 135236.00359199077046. 1 AU40622-40659Skilled artisans will recognize the examples provided herein have many useful alternatives and fall within the scope of embodiments of the invention.

[0087] It is to be understood that the invention is not limited in its application to the details of construction and the arrangement of components set forth in the following description or illustrated in the attached drawings. The invention is capable of other embodiments and of being practiced or of being carried out in various ways. Also, it is to be understood that the phraseology and terminology used herein is for the purpose of description and should not be regarded as limiting. For example, the use of “including,” “comprising,” or “having” and variations thereof herein is meant to encompass the items listed thereafter and equivalents thereof as well as additional items.

[0088] Also as used herein, ordinal numbers are used for convenience of presentation only and are generally presented in an order that corresponds to the order in which particular features are introduced in the relevant discussion. Accordingly, for example, a “first” feature may not necessarily have any required structural or sequential relationship to a “second” feature, and so on. Further, similar features may be referred to in different portions of the discussion by different ordinal numbers. For example, a particular feature may be referred to in some discussion as a “first” feature, while a similar or substantially identical feature may be referred to in other discussion as a “third” feature, and so on.

[0089] Unless otherwise specified or limited, the terms “about” and “approximately,” as used herein with respect to a reference value, refer to variations from the reference value of ± 15% or less (e g., ± 10%, ± 5%, etc.), inclusive of the endpoints of the range.

[0090] The description of the different advantageous embodiments has been presented for purposes of illustration and description and is not intended to be exhaustive or limited to the embodiments in the form disclosed. Many modifications and variations will be apparent to those of ordinary skill in the art. Further, different advantageous embodiments may provide different advantages as compared to other advantageous embodiments. The embodiment or embodiments selected are chosen and described in order to best explain the principles of the embodiments, the practical application, and to enable others of ordinary skill in the art to understand the disclosure for various embodiments with various modifications as are suited to the particular use contemplated.24QB' 135236.00359199077046. 1 AU40622-40659

Claims

CLAIMSWhat is claimed is:

1. A valve, comprising: a valve body defining a first seat surrounding an orifice; a valve element movably disposed within the valve body, the valve element moving between a first position where the valve element is engaged with the first seat to close the orifice, and a second position where the valve element is disengaged from the first seat to open the orifice; a nut movably coupled within the valve body, the nut engaged with the valve element such that relative rotation between the nut and the valve element causes the valve element to move between the first position and the second position; an actuator that applies torque to one of the valve element and the nut to rotate the one of the valve element and the nut relative to the other of the valve element and the nut; and an anti-jamming feature that dissipates torque from the actuator that applied to the one of the valve element and the nut when the valve element is moved into the first position from the second position.

2. The valve of claim 1, wherein the anti -jamming feature allows the actuator to build torque prior to the valve element disengaging the first seat when the valve element is moved towards the second position from the first position.

3. The valve of claim 2, wherein the actuator rotates the nut relative to the valve element, the actuator including a torsion rod that that is coupled to the nut.

4. The valve of claim 3, wherein the actuator is a motor having a stator and a rotor that is rotated by the stator about an axis, the nut and the valve element being concentric with the axis such that the nut rotates about the axis and the valve element translates along the axis.

5. The valve of claim 4, wherein the rotor includes an outer shell, a magnet coupled to the outer shell, and the torsion rod coupled to the outer shell by a beam, the torsion rod extending through the outer shell and allowing the outer shell to rotate relative to the nut.25QB' 135236.00359\99077046.1 AU40622-406596. The valve of claim 5, wherein the outer shell, the beam, and the torsion rod are formed as a unitary component.

7. The valve of claim 2, wherein the nut is secured to the valve body via a bendable tab of the valve body.

8. The valve of claim 7, wherein the nut includes a flange positioned between a first bearing and a second bearing, the first bearing positioned between the bendable tab and the flange.

9. The valve of claim 2, further comprising a seal positioned between the nut and the first seat, the valve element slidably extending through the seal such that a first end of the valve element that engages the first seat is on a first side of the seal and a second end of the valve element that engages the nut is on a second side of the seal that is opposite the first side.

10. The valve of claim 9, wherein the valve body includes a first valve body defining the first seat, and a second valve body coupled to the nut and the actuator, the seal secured between the first valve body and the second valve body.

11. The valve of claim 9, wherein the valve element includes a channel extending through the valve element from the first end to the second end to communicate pressure at the first end of the valve element to the second end of the valve element when the valve element is in the first position.

12. The valve of claim 2, wherein the nut is rotationally fixed to the valve body and the actuator rotates the valve element, and wherein the anti -jamming feature includes a first resilient member positioned between a first end of the nut and the valve body, and a second resilient member positioned between a second end of the nut and the valve body, such that the nut is translatable relative to the valve element and the valve body.26QB' 135236.00359199077046. 1 AU40622-4065913. The valve of claim 12, wherein the nut translates away from the first seat to compress the first resilient member when the valve element moves to the first position from the second position, and the nut translates toward the first seat to compress the second resilient member when the valve element away from the first position toward the second position, such that the nut translates relative to the valve element in response to rotation of the valve element.

14. The valve of claim 1, wherein the valve includes a second seat, the valve element engaging the second seat in the second position, and wherein the anti-jamming feature dissipates torque from the actuator applied to the one of the valve element and the nut when the valve element is moved into the second position from the first position, and allows the actuator to build torque prior to the valve element disengaging the second seat when the valve element is moved towards the first position from the second position.

15. The valve of claim 14, wherein the actuator includes a stator, a rotor, and a rotor tube between the stator and the rotor, the rotor tube defining the second seat.27QB' 135236.00359199077046. 1 AU40622-4065916. An electronic expansion valve comprising: a valve body defining a first seat surrounding an orifice; a valve element movably disposed within the valve body, the valve element moving between a first position where the valve element is engaged with the first seat to close the orifice, and a second position where the valve element is disengaged from the first seat to open the orifice; an actuator that moves the valve element between the first position and the second position; and an anti-jamming feature that absorbs energy from the actuator to allow the actuator to move relative to the valve element when the valve element is stopped in the first position, such that the anti -jamming feature reduces force applied between the valve element and the first seat when the valve element engages the first seat.

17. The electronic expansion valve of claim 16, wherein the anti -jamming feature allows the actuator to build momentum to increase the force applied to the valve element when the valve element disengages the first seat.

18. The electronic expansion valve of claim 16, wherein the anti-jamming feature is disposed in the valve body.

19. The electronic expansion valve of claim 16, wherein the anti-jamming feature is disposed in the actuator.

20. The electronic expansion valve 16, wherein the actuator defines a second seat and the pin engages the second seat in the second position, and wherein the anti -jamming feature absorbs energy from the actuator to allow the actuator to move relative to the valve element when the valve element is stopped in the second position, such that the anti -jamming feature reduces force applied between the valve element and the second seat when the valve element engages the second seat.28QB' 135236.00359X99077046. 1 AU40622-40659

Images