Thermal System

Abstract

A thermal system includes an accumulator having a housing defining a housing cavity. The accumulator includes a low pressure inlet line, a first low pressure outlet line, and a second low pressure outlet line.

Description

FIELD

The present disclosure relates generally to thermal systems.

BACKGROUND

Thermal systems are often used for cooling Some thermal systems include an accumulator to store additional refrigerant to support the dynamic demands placed on the system and to ensure adequate refrigerant amount for the life of the system. An evaporator is commonly used in the system to absorb heat into the refrigerant. The existence of refrigerant in a gaseous phase in the evaporator reduces the heat transfer or heat absorption capacity of the evaporator reducing its efficiency and the overall cooling capacity of the thermal system.

SUMMARY

A first aspect of the disclosure is a thermal cycle system. The thermal cycle system includes a high pressure refrigerant inlet line, a high pressure refrigerant outlet line, and an accumulator including a housing defining a housing cavity configured to store a refrigerant. A low pressure refrigerant inlet line and a first low pressure refrigerant outlet line are in communication with the housing cavity. A second low pressure refrigerant outlet line includes an inlet end positioned in the housing cavity in communication with the refrigerant and is configured to transfer the refrigerant in a liquid phase from the accumulator to an evaporator. An internal heat exchanger is positioned in the housing cavity in communication with the high pressure refrigerant inlet line and the high pressure refrigerant outlet line and is configured to expel heat to the housing cavity.

In one example of the thermal cycle system according to the first aspect of the disclosure, the thermal cycle system includes a vortex breaker positioned in the housing cavity and is configured to prevent entrainment of the refrigerant in a gaseous phase into the second low pressure refrigerant output line.

In one example of the first aspect of the disclosure, the accumulator includes a separator container positioned in the housing cavity. The separator container includes a bottom portion and a top portion, and defines a separator container cavity. The separator container is configured to store and promote separation of the refrigerant in a gaseous phase and the refrigerant in the liquid phase in the separator container cavity. The refrigerant in the gaseous phase is positioned toward the top portion of the separator container above the refrigerant in the liquid phase.

In one example of the first aspect of the disclosure, the separator container is configured to further store and promote separation of oil from the refrigerant in the gaseous phase and the refrigerant in the liquid phase. The oil is positioned toward the bottom portion of the separator container below the refrigerant in the liquid phase.

A second aspect of the disclosure is an accumulator. The accumulator includes a housing defining a housing cavity configured to store a refrigerant. The accumulator includes a low pressure refrigerant inlet line in communication with the housing cavity and a first low pressure refrigerant outlet line in communication with the housing cavity. A second low pressure refrigerant outlet line includes an inlet end positioned in the housing cavity in communication with the refrigerant in a liquid phase. The second low pressure refrigerant outlet line is configured to transfer the refrigerant in the liquid phase from the housing to an evaporator. A vortex breaker is positioned in the housing cavity and is configured to prevent entrainment of the refrigerant in a gaseous phase into the second low pressure refrigerant outlet line.

In one example of the accumulator according to the second aspect of the disclosure, the accumulator includes a high pressure refrigerant inlet line and a high pressure refrigerant outlet line. An internal heat exchanger is positioned in the housing cavity in communication with the high pressure refrigerant inlet line and the high pressure refrigerant outlet line. The internal heat exchanger is configured to expel heat to the housing cavity.

A third aspect of the disclosure is a thermal cycle system. The thermal cycle system includes a compressor configured to transfer a refrigerant under pressure, a gas cooler in communication with the compressor, and an accumulator in communication with the gas cooler. The accumulator includes a housing defining a housing cavity configured to store the refrigerant. An internal heat exchanger is positioned in the housing cavity in communication with the gas cooler configured to expel heat from the refrigerant received from the gas cooler to the housing cavity. The thermal cycle system includes a first low pressure refrigerant outlet line, and a second low pressure refrigerant outlet line. The second low pressure refrigerant outlet line includes an inlet end positioned in the housing cavity in communication with the refrigerant in a liquid phase. An ejector is in communication with the internal heat exchanger and configured to lower a pressure and a temperature of the refrigerant received from the internal heat exchanger. The ejector including an ejector outlet line in communication with the housing cavity of the accumulator. An evaporator is in communication with the second low pressure refrigerant outlet line and is configured to receive the refrigerant in the liquid phase through the second low pressure refrigerant outlet line. The evaporator is in communication with the ejector. A valve is positioned in the second low pressure refrigerant outlet line upstream of the evaporator. The valve is configured to meter the flow of the refrigerant in the liquid phase to the evaporator.

In one example of the third aspect of the disclosure, the thermal cycle system includes a vortex breaker positioned in the housing cavity configured to prevent entrainment of the refrigerant in a gaseous phase into the second low pressure refrigerant outlet line.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic illustration of an example of a thermal cycle system.

FIG. 2 is an enlarged view of an area A of FIG. 1 according to a first example.

FIG. 3 is an enlarged perspective view of an area B of FIG. 2.

FIG. 4 is an alternate example of the area B of FIG. 3.

FIG. 5 is an enlarged view of the area A of FIG. 1 according to a second example.

DETAILED DESCRIPTION

Conventional thermal cycle systems for vehicles typically include a compressor that provides high temperature and high pressure refrigerant in a gaseous phase to a gas cooler or condenser. The condenser receives the refrigerant from the compressor, reduces the temperature of the high pressure refrigerant, and changes the gaseous phase refrigerant to a mixture of refrigerant in a liquid phase and refrigerant in a gaseous phase. An expansion valve receives the refrigerant from the gas cooler, lowers the pressure, and further reduces the temperature, thereby changing more of the refrigerant to a gaseous phase. An evaporator receives the low pressure, low temperature refrigerant from the expansion valve and absorbs heat into the mixture of refrigerant in the gaseous phase and refrigerant in the liquid phase inside the evaporator. The refrigerant mixture turns more of the refrigerant to the gaseous phase.

The thermal properties of liquids and gasses generally provide that liquid has a higher heat transfer capability or heat absorbing capacity, and a lower enthalpy, than gas. With respect to the mixture of refrigerant in a liquid phase and refrigerant in a gaseous phase, the enthalpy of the mixture depends on the ratio of liquid phase refrigerant to gaseous phase refrigerant. Thus, the more refrigerant in the gaseous phase in the evaporator reduces the heat absorbing efficiency of the evaporator and reduces the overall cooling capacity of the thermal cycle system.

The disclosure including FIGS. 1-5 is directed to examples of thermal cycle systems and an accumulator which in part serves to store refrigerant for use by the thermal cycle system. The thermal cycle system or accumulator includes a first low pressure refrigerant outlet line and a second low pressure refrigerant outlet line. The second low pressure refrigerant outlet line provides refrigerant in a liquid phase to the evaporator to increase the efficiency of the evaporator and the overall cooling capacity of the thermal cycle system.

FIG. 1 is a schematic illustration of one example of a thermal cycle system 100. In the example, the thermal cycle system 100 is a heat and cold generating system that uses an electric powered refrigerant cycle (e.g., a vapor-compression refrigeration cycle) in which a refrigerant is circulated through the thermal cycle system 100. In one example described further below, the thermal cycle system is configured to operate using a CO₂-based R744 refrigerant. In one example, the thermal cycle system can be used in a vehicle to provide heating and cooling for vehicle systems and subsystems including battery cooling, computing device cooling, actuator cooling, and climate control for the cooling or heating of a vehicle passenger compartment. The thermal cycle system 100 may be used in applications other than vehicles or for other systems of vehicles.

A first example of the thermal cycle system 100 is shown in FIG. 1. The thermal cycle system 100 includes an accumulator 102 and a compressor 104 having a compressor outlet line 106 configured to transfer a refrigerant 107 through the thermal cycle system 100. The compressor 104 is in communication with a gas cooler 108 (e.g., a condenser) through the compressor outlet line 106. In one example, the compressor outlet line 106 is a hollow tube or tubing made from a polymer. In an alternate example, a synthetic rubber or other elastomer may be used. Other materials for the compressor outlet line 106, for example steel or aluminum tubing, may be used. The other refrigerant transfer lines described and illustrated below may be of the same or similar materials as described above. In one example the refrigerant 107 is a CO₂-based R744 refrigerant. Other types of refrigerant may be used.

In the example, the refrigerant 107 passing through the compressor 104 is in the form of the refrigerant in a gaseous phase 110 (i.e., predominantly in a gaseous state or phase). The refrigerant in the gaseous phase 110 exits the compressor 104 at a high temperature and at a high pressure and is transferred to the gas cooler 108. The gas cooler 108 reduces the temperature of the refrigerant in the gaseous phase 110 whereby at least a portion of the refrigerant in the gaseous phase 110 is changed to the refrigerant in a liquid phase 112 thereby reducing the enthalpy (kJ/kg) of the refrigerant 107. It is understood that the refrigerant in the gaseous phase 110 and the refrigerant in the liquid phase 112 is the refrigerant 107 just in a different phase or state (i.e., gas or liquid). It is further understood the refrigerant 107 exiting the gas cooler 108 may be predominately refrigerant in the gaseous phase 110, or refrigerant in the liquid phase 112, or combinations thereof.

In one example, the refrigerant 107 exits the gas cooler 108 at high pressure through a gas cooler outlet line 113. In one example, the gas cooler outlet line 113 is in communication with a high pressure refrigerant inlet line 114. As best seen in the FIGS. 1 and 2 example, the thermal cycle system 100 includes an internal heat exchanger 116 positioned inside the accumulator 102 and is in communication with the high pressure refrigerant inlet line 114. In one example, the internal heat exchanger 116 is a segment or extension of the high pressure refrigerant inlet line 114 (e.g., a tube or tubing) routed through the accumulator 102 as further discussed below. In an alternate example (not shown), the internal heat exchanger 116 may take other forms, for example a separate or alternately configured structure that is in communication with the high pressure refrigerant inlet line 114.

As best seen in FIG. 2, the refrigerant 107 passing through the internal heat exchanger 116 is refrigerant at a high pressure and a relatively high temperature 217 (i.e., still in the high pressure side of the thermal cycle system 100). In one example, the internal heat exchanger 116 expels heat from the refrigerant at the high pressure and the relatively high temperature 217 into the accumulator 102 as further described below. In one example, there is a reduction in the enthalpy of the refrigerant 107 passing through the high pressure refrigerant inlet line 114 into and through the internal heat exchanger 116.

Referring to the FIG. 1 example, the thermal cycle system 100 includes a high pressure refrigerant outlet line 118 in communication with the internal heat exchanger 116. The high pressure refrigerant outlet line 118 transfers the refrigerant 107 exiting the internal heat exchanger 116 and the accumulator 102 to an ejector high pressure inlet line 120 in communication with an ejector 122 as generally shown.

In the FIG. 1 example, the compressor 104, the gas cooler 108, the internal heat exchanger 116, and the ejector high pressure inlet line 120 are on the high pressure side of the thermal cycle system 100. Refrigerant 107 exiting the compressor 104 is at a higher pressure and higher temperature than refrigerant 107 entering the compressor 104. In one example, the pressure of the refrigerant 107 traveling between the compressor 104 and the ejector 122 remains relatively constant. In one example, there is a gradual reduction in the enthalpy of the refrigerant 107 between exiting the compressor 104 and entering the ejector 122.

In one example, the ejector 122 is configured to lower the pressure and the temperature of the refrigerant 107 entering through the ejector high pressure inlet line 120. In one example, the ejector 122 is configured to function in part as an expansion valve to greatly reduce the temperature and the pressure of the refrigerant 107. In one example, the ejector 122 is configured to diffuse the received refrigerant in the gaseous phase 110 and the refrigerant in the liquid phase 112. The ejector 122 transfers or propels the refrigerant 107 at a low pressure and at a high velocity through an ejector outlet line 124 downstream (i.e., to the low pressure side of the thermal cycle system 100). It is understood that the ejector 122 may take other forms and configurations, for example a conventional expansion valve, or function in alternate manners to reduce the temperature and pressure of the refrigerant 107 as known by persons skilled in the art.

Referring to the FIGS. 1 and 2 example, the thermal cycle system 100 includes a low pressure refrigerant inlet line 128 in communication with the ejector outlet line 124 configured to receive the refrigerant 107 from the ejector 122. The pressure and temperature of the refrigerant exiting the ejector 122 through the ejector outlet line 124 and entering the accumulator 102 through the low pressure refrigerant input line 128 are lower than the refrigerant 107 entering the ejector 122.

In the FIGS. 1 and 2 example, the accumulator 102 includes a housing 130 defining a housing cavity 132 configured to store the refrigerant 107. In one example, the housing 130 receives the refrigerant 107 through the low pressure refrigerant inlet line 128 wherein the refrigerant 107 includes the refrigerant in the gaseous phase 110 or the refrigerant in the liquid phase 112, or a combination thereof.

In one example, and as discussed further below, the accumulator 102 through use of the housing 130 is configured to store and promote the separation of the refrigerant in the gaseous phase 110 and the refrigerant in the liquid phase 112 in the housing cavity 132. In one example, the refrigerant in the liquid phase 112 is positioned or settles through the force of gravity or the properties of the refrigerant 107 below the refrigerant in the gaseous phase 110 as generally shown in FIGS. 1 and 2 and further described below. In one example, this separation of the refrigerant in the liquid phase 112 from the refrigerant in the gaseous phase 110 lowers the enthalpy of the refrigerant (i.e., the enthalpy of the refrigerant in the liquid phase 112 is lower than the enthalpy of the refrigerant in the gaseous phase 110).

In one example, the housing 130 is configured in a cylindrical shape and may be made of metal (e.g., steel or aluminum). Other materials, shapes, sizes and configurations for housing 130 may be used. As discussed further below, a separator container 133 is positioned inside the housing cavity 132 of the housing 130.

In one example of the thermal cycle system 100 shown in FIGS. 1 and 2, the refrigerant 107 may include an oil 134 configured to lubricate the compressor 104. The accumulator 102, through use of the housing 130, is further configured to store and promote the separation of the oil 134 from the refrigerant in the gaseous phase 110 and the refrigerant in the liquid phase 112. The oil 134 is positioned or settles at the bottom of the accumulator 102, for example through the force of gravity or the properties of the oil 134 (e.g., material density) and the refrigerant 107. Thus, the refrigerant in the liquid phase 112 is positioned above the oil 134 in the accumulator 102 as generally shown and further described below. It is understood that the thermal cycle system 100 may not include oil 134 in the refrigerant 107.

Still referring to the FIGS. 1 and 2 example, the thermal cycle system 100 or the accumulator 102 further includes a first low pressure refrigerant outlet line 138 in communication with the housing cavity 132. In one example shown in FIGS. 1 and 2, the first low pressure refrigerant outlet line 138 is positioned toward a top portion of the housing 130 for receipt of the refrigerant in the gaseous phase 110 and to transfer the refrigerant in the gaseous phase 110 to the compressor 104. In one example, the refrigerant in the gaseous phase 110 positioned in the housing cavity 132 is drawn under a vacuum force by the compressor 104 from the housing cavity 132 through the first low pressure refrigerant outlet line 138 to the compressor 104. The temperature and pressure of the refrigerant 107 entering the compressor 104 through the first low pressure refrigerant outlet line 138 is lower than the temperature and pressure of the refrigerant 107 entering the ejector 122. In an alternate example (not shown), the first low pressure refrigerant outlet line 138 is alternately positioned on the housing 130 (e.g., positioned on the vertical side or bottom of the housing 130).

In the FIGS. 1 and 2 example, and as further discussed below, the thermal cycle system 100 further includes a second low pressure refrigerant outlet line 140. As best seen in FIG. 2, the second low pressure refrigerant outlet line 140 includes an inlet end 242 positioned in the housing cavity 132 in communication with the refrigerant 107. In the FIGS. 1 and 2 example, the inlet end 242 is positioned and in communication with the refrigerant in the liquid phase 112 that has separated or settled below the refrigerant in the gaseous phase 110 and, if used in refrigerant 107, above the oil 134. The second low pressure refrigerant outlet line 140 is configured to transfer the refrigerant in the liquid phase 112 from the accumulator 102 to an evaporator 144 further described below.

Referring to the FIG. 1 example, the thermal cycle system 100 further includes a valve 146 positioned in the second low pressure refrigerant outlet line 140 upstream of the evaporator 144. The valve 146 is configured to control or meter the flow of the refrigerant in the liquid phase 112 to the evaporator 144. In one example, the valve 146 is an electrically powered and electrically operated or actuated valve in communication with a control system 148 discussed further below. One or more sensors (not shown) may be used to monitor the position of the valve 148 (i.e., in an open or closed position), or the volume or velocity of flow of the refrigerant in the liquid phase 112, or the temperature of the refrigerant in the liquid phase 112, or a combination thereof. Additional or other system metrics may be monitored by sensors.

In one example, the refrigerant in the liquid phase 112 that enters the inlet end 242 is all refrigerant in the liquid phase 112, or predominantly all refrigerant in the liquid phase 112. In the example, due to the passage of the refrigerant through the internal heat exchanger 116 and separation of the refrigerant in the liquid phase 112 from refrigerant in the gaseous phase 110 in the accumulator, the enthalpy of the refrigerant has been lowered two times in two different ways. In an alternate example, a small amount of the refrigerant in the gaseous phase 110 may be included or also pass through the inlet end 242 along with the refrigerant in the liquid phase 112.

The pressure and temperature of the refrigerant 107 entering the evaporator 144 is lower than the pressure and the temperature of the refrigerant 107 entering the ejector 122.

Referring to the FIG. 1 example, the valve 146 is in communication with an evaporator intake line 150 in communication with the evaporator 144 as generally shown. An evaporator outlet line 152 is positioned downstream of the evaporator 144 and is in communication with the evaporator 144 as generally shown. An ejector low pressure inlet line 154 is in communication with the evaporator outlet line 152 and the ejector 122. The ejector low pressure inlet line 154 is configured to transfer the refrigerant 107 exiting the evaporator 144, for example the refrigerant in the gaseous phase 110, the refrigerant in the liquid phase 112, or combinations thereof. In one example, the ejector 122 receipt of refrigerant 107 through the ejector high pressure inlet line 120 creates a vacuum force to draw the flow of refrigerant 107 from the evaporator 144 through the ejector low pressure inlet line 154 and into the ejector 122.

In one example, the ejector 122 is configured to mix the refrigerant 107 from the evaporator 144 received through the ejector low pressure inlet line 154 and the refrigerant 107 received through the ejector high pressure inlet line 120 resulting in the exit of the refrigerant 107 through the ejector outlet line 124 toward the low pressure refrigerant inlet line 128 to the accumulator 102 as described above and illustrated in FIG. 1. It is understood that different configurations or routing of the inlet and outlet lines between the gas cooler 108, the accumulator 102, the evaporator 144 and the ejector 122 may be used to suit the particular application and performance requirements of the thermal cycle system 100.

Referring to FIG. 2, an example of the thermal cycle system 100 and the accumulator 102 is shown. In the example, the accumulator 102 includes the separator container 133 positioned in the housing cavity 132. The separator container 133 includes a bottom portion 260, a top portion 262 and defines a separator container cavity 263. In the example, the separator container 133 is configured to store and promote separation of the refrigerant in the gaseous phase 110 and the refrigerant in the liquid phase 112 in the separation container cavity 263. In the example, the low pressure refrigerant inlet line 128 is configured to transfer the refrigerant 107 received from the ejector 122 into the separator container cavity 263.

As described above, under the force of gravity or through the material properties of the refrigerant 107, the refrigerant in the liquid phase 112 separates or settles below the refrigerant in the gaseous phase 110. The refrigerant in the gaseous phase 110 rises or is positioned toward the top portion 262 of the separator container 133 above the refrigerant in the liquid phase 112.

In one example, the separator container 133 is cylindrical shaped and may be made of polymers, composite materials, or metal (e.g., steel or aluminum). Other materials, sizes, shapes and configurations for separator container 133 may be used.

In the FIGS. 1 and 2 example as described above, where the refrigerant 107 includes oil 134, the separator container 133 is further configured to store and promote the separation of the oil 134 from the refrigerant in the gaseous phase 110 and the refrigerant in the liquid phase 112. In the example, the oil 134 is positioned, gravitates or settles toward the bottom portion 260 of the separator container 133 below the refrigerant in the liquid phase 112 as generally shown. In a separated state shown for illustrative purposes, the oil 134 includes an oil top surface 264, and the refrigerant in the liquid phase 112 includes a liquid refrigerant top surface 265.

In one example, additional structures (not shown) may be included as part of the separator container 133 (or housing 130) or be positioned in the separator container cavity 263 (or housing cavity 132) to promote or maintain separation of the oil 134, the refrigerant in the liquid phase 112, and the refrigerant in the gaseous phase 110. In one example, a baffle or perforated structure may be positioned in the separator container cavity 263 and used to promote separation. In another example wherein the separator container 133 is cylindrical shaped, and due to the velocity of the refrigerant 107 entering through the low pressure refrigerant inlet line 128, a centrifugal separation structure (e.g., a cyclonic structure or component) may be used which urges more dense materials, oil 134 for example, toward a center of the circular swirling or revolving refrigerant 107 and along with the force of gravity downward toward the bottom portion 260 of the separator container 133. In another example, a membrane material, for example GORE-TEX®, may be used wherein the membrane allows materials or substances to pass one-way through the membrane which are then prevented from passing back through the membrane. Other structures may be used to promote separation as known by persons skilled in the art.

In another example, the accumulator 102 may include a filter (not shown) to remove impurities or particulates from the refrigerant 107 passing through or positioned in the housing cavity 132 or the separator container cavity 263, or a combination thereof. In another example, water, water vapor or moisture may be removed from the refrigerant 107 passing through or positioned in the housing cavity 132 or the separator container cavity 263, or a combination thereof. In one example, desiccant is positioned in the accumulator 102 and is used to absorb or remove water or moisture from the refrigerant 107.

In the FIGS. 1 and 2 example, and as best seen in FIG. 2, the accumulator 102 includes an oil recovery tube 268 positioned in the separator container cavity 263 and connected to the separator container 133. In the example, the oil recovery tube 268 includes an inlet end 269 positioned in the separator container cavity 263 above the liquid refrigerant top surface 265 and in communication with the refrigerant in the gaseous phase 110. The oil recovery tube includes a lower portion 270 positioned in the oil 134 below the oil top surface 264 as generally shown. The oil recovery tube 268 includes an outlet end 271 positioned exterior to the separator container 133 in the housing cavity 132. An oil recovery orifice 272 is positioned at the lower portion 270 of the oil recovery tube 268 in communication with the oil 134.

In one example, the oil recovery tube 268 is generally “U” shaped and is a narrow or small diameter hollow tube or pipe made from plastic. Other materials, shapes, sizes and configurations described for the oil recovery tube 268 and the refrigerant 107 transfer lines may be used.

As shown in FIG. 2, the inlet end 269 of the oil recovery tube 268 is positioned in and in communication with the refrigerant in the gaseous phase 110 that rises toward the top portion 262 of the separator container 133. The lower portion 270 and oil recovery orifice 272 are positioned below the oil top surface 264 and in communication with the oil 134 that settles toward the bottom portion 260 of the separator container 133. The oil recovery tube 268 is configured to transfer the refrigerant in the gaseous phase 110 from the separator container 133 and the oil 134 received through the oil recovery orifice 272 to the housing cavity 132 for further transfer through the first low pressure refrigerant outlet line 138 to the compressor 104.

In the example, due to the described and illustrated configuration of the oil recovery tube 268, refrigerant in the gaseous phase e110 positioned in the top portion 262 of the separator container 133 in the separator container cavity 263 is drawn down into the inlet end 269 of the oil recovery tube 268, passes through the lower portion 270 and out the outlet end 271 as generally illustrated. Oil 134 adjacent to the oil recovery orifice 272 is also drawn into the oil recovery tube 268 through the oil recovery orifice 272 for transfer through the oil recovery tube 268 and through the outlet end 271.

In the FIGS. 1 and 2 example, the refrigerant in the gaseous phase 110, and small amounts of oil 134 that are suspended or airborne in the refrigerant in the gaseous phase 110 exit the outlet end 271 of the oil recovery tube 268 into the housing cavity 132. It is understood that refrigerant in the gaseous phase 110 exiting the outlet end 271 of the oil recovery tube 268 may also contain small amounts of refrigerant in the liquid phase 112. The refrigerant 107 exiting the outlet end 271 as described fills, disburses or circulates around the housing cavity 132 in communication with the internal heat exchanger 116.

As best seen in FIG. 2, heat 274 is expelled by the internal heat exchanger 116 into the housing cavity 132 to elevate a temperature of the refrigerant in the gaseous phase 110, the refrigerant in the liquid phase 112, or the oil 134, or combinations thereof, positioned in the housing cavity 132 or the separator container 133. In one example, heat 274 is expelled by the internal heat exchanger 116 into the housing cavity 132 to elevate a temperature of the refrigerant in the gaseous phase 110 positioned in the housing cavity 132.

In one example, the high pressure refrigerant inlet line 114 is configured to transfer the refrigerant in the liquid phase 112, the refrigerant in the gaseous phase 110, or combinations thereof, under high pressure and high temperature to the internal heat exchanger 116. The internal heat exchanger 116 is configured to expel heat 274 to the housing cavity 132. The internal heat exchanger 116 expels the heat 274 as a result of the refrigerant at a high pressure and the relatively high temperature 217 passing through the internal heat exchanger 116 positioned in the accumulator 102 which stores refrigerant 107 at a low pressure and at a low or cold temperature (relative to the refrigerant on the high pressure side of the thermal cycle system 100 as described above). The transfer of heat 274 from the refrigerant 107 from thermal cycle system 100 warm high pressure side to the refrigerant 107 on the cold low pressure side in the accumulator 102 increases the efficiency and overall cooling capacity of the thermal cycle system 100.

Referring to the FIG. 2 example and as described above, the refrigerant 107 enters the accumulator 102 through the low pressure refrigerant inlet line 128 into the separator container cavity 263, or alternately into the housing cavity 132 where a separator container 133 is not used, at a high or relatively high velocity. In one example where the separator container 133 is cylindrically shaped, this may produce a circular swirling or vortex form of flow of the refrigerant 107 inside the separator container cavity 263. In the FIGS. 1 and 2 example where the refrigerant 107 includes separated refrigerant in the gaseous phase 110 and refrigerant in the liquid phase 112, the vortex and the force of gravity may force a flow of the refrigerant in the gaseous phase 110 to extend downward toward the bottom portion 260 of the separator container 133 into the refrigerant in the liquid phase 112 that is stored or settled in the separator container 133 (i.e., the refrigerant in the gaseous phase 110 extends below what would otherwise be the liquid refrigerant top surface 265).

As described above, inlet end 242 of the second low pressure refrigerant outlet line 140 is positioned in the refrigerant in the liquid phase 112 and in communication therewith. As described above, the second low pressure refrigerant outlet line 140 is configured to transfer refrigerant in the liquid phase 112 from the accumulator 102 to the evaporator 144.

Referring to the FIG. 2 example, a vortex breaker 276 is positioned in the housing cavity 132 (or separator container cavity 263 as shown) and is configured to prevent or minimize entrainment of the refrigerant in the gaseous phase 110 into the second low pressure refrigerant outlet line 140. As described above and illustrated in FIGS. 2 and 3, the vortex breaker 276 is positioned in the refrigerant in the liquid phase 112 and in communication therewith. As best seen in the FIG. 2 example, the vortex breaker 276 is positioned above the oil top surface 264 and below the liquid refrigerant top surface 265.

In the example shown in FIG. 3, the vortex breaker 276 includes a support 378 connected to the inlet end 242 of the second low pressure refrigerant outlet line 140. The vortex breaker 276 further includes a plate 379 connected to the support 378. The support 378 and the plate 379 define an opening 380 in communication with the second low pressure refrigerant outlet line 140 configured to allow passage of the refrigerant in the liquid phase 112 into the second low pressure refrigerant outlet line 140 through the inlet end 242.

In the FIG. 3 example of the vortex breaker 276, the support 378 includes legs 381 (four shown) that are each connected to the plate 379 and extend to the second low pressure refrigerant outlet line 140 and engage the second low pressure refrigerant outlet line 140 to connect the vortex breaker 276 thereto. The legs 381 extend parallel to an axis 382 that extends along a centerline or longitudinal axis of the second low pressure refrigerant outlet line 140 as generally shown. The legs 381 and the plate 379 defining liquid refrigerant openings 380A angularly between the legs 381 about the axis 382 in communication with the second low pressure refrigerant outlet line 140 configured to allow passage of the refrigerant in the liquid phase 112 into the second low pressure refrigerant outlet line 140. In one example, the vortex breaker 276 is operable to prevent, deter or disrupt the formation of a vortex from forming in the refrigerant in the liquid phase 112 or entrainment of the refrigerant in the gaseous phase 110 from entering the second low pressure refrigerant outlet line 140, or combinations thereof.

In one example, the plate 379 is configured as a continuous surface (i.e., a solid surface without openings or passages through the plate 379). In one example, the support 378 and the plate 379 are made from plastic. Alternate materials, for example steel or aluminum, and alternate configurations may be used. Alternate configurations for the support 378, the plate 379 and the vortex breaker as a whole, may be used.

In one example, the support 378 is connected to the second low pressure refrigerant outlet line 140 through a structure (not shown) providing for a clip-on connection to securely connect the vortex breaker 276 to the second low pressure refrigerant outlet line 140. In alternate examples, the support 378 or the legs 381 may include formations, for example sharp barbs, that engage an inner surface of the inlet end 242 to securely connect the vortex breaker 276 to the second low pressure refrigerant outlet line 140. Other formations or methods to create engagement or an interference fit between the vortex breaker 276 and the second low pressure refrigerant outlet line 140 may be used. In an alternate example, adhesive or mechanical fasteners may be used.

Referring to the FIG. 3 example, the vortex breaker 276 further includes a sidewall 384 (one shown) connected to the support 378 or the plate 379, or combinations thereof. The sidewall 384 is positioned in the opening 380 and is configured to minimize or prevent entrainment of the refrigerant in the gaseous phase 110 into the second low pressure refrigerant outlet line 140 or prevent or disrupt a vortex flow of the refrigerant 107 described above, or combinations thereof. In one example, the sidewall 384 is removably connected to the support 378 or the plate 379, or a combination thereof.

In one example, the sidewall 384 is configured to removably clip-on (e.g., a snap-on or clip-on engagement or interference fit) and securely connect to the support 378 or the plate 379, or a combination thereof. Other methods or structures to connect the sidewall 384 to the support 378, the plate 379, the second low pressure refrigerant outlet line 140, or combinations thereof, may be used.

The removable engagement allows for flexibility in the positioning of the sidewall 384 relative to the support 378 to adjust or fine tune the position or location of the sidewall 384 to best prevent or minimize entrainment or passage of refrigerant in the gaseous phase 110 into the second low pressure refrigerant outlet line 140, or to disrupt a vortex flow of refrigerant 107 as described above.

In the FIG. 3 example, the sidewall 384 is configured as a continuous surface (i.e., a solid surface without openings of passages through the sidewall 384. In one example, the sidewall is made from plastic. Alternate materials, for example steel, aluminum composites, fabrics, or membranes described above, may be used. It is understood that alternate, configurations, sizes, shapes, openings, slots, or mesh screens for sidewall 384 may be used. It is further understood that additional numbers of the sidewall 384 and the position or location of the sidewall 384 relative to the support 378 or the second low pressure refrigerant outlet line 140 may be used.

Referring to FIG. 4, an alternate example of the vortex breaker 276A is shown. The vortex breaker 276A includes the same or substantially similar support 378, openings 380, legs 381, functions, and alternatives thereto, as described above for vortex breaker 276 with the exception of the plate 379. In the FIG. 4 example, the second low pressure outlet line 140 is a circular tube or pipe having a diameter 483. In the FIG. 4 example, plate 379A includes a diameter 486 that is larger than the diameter 483 of the second low pressure outlet line 140. In one example, the diameter 486 of the plate 379A is about two times as large (i.e., double) as the diameter 483 of the second low pressure outlet line 140. Alternate sizes, shapes, or diameters, larger or smaller, for the plate 379A and plate 379 may be used to suit the particular application and performance requirements.

In an alternate example of the vortex breaker 276 (not shown), the vortex breaker 276 may be integral with the second low pressure refrigerant outlet line 140. In one example, the inlet end 242 may be closed and through holes or openings may be provided in the walls of the second low pressure refrigerant outlet line 140. In the example, the material between the through holes may serve as the sidewall 384 and the through holes serving as the liquid refrigerant openings 380A allowing passage of the refrigerant in the liquid phase 112 to the second low pressure refrigerant outlet line 140 as described above. Alternate structures may be used to suit the particular application. It is understood that the thermal cycle system 100 can be implemented without the vortex breaker 276. It is understood that the vortex breaker 276 can be used in any variations or configurations of the thermal cycle system 100 described herein. It is understood that the vortex breaker 276 can be used in combination with the separator container 133 or where a separator container 133 is not used, in configurations where oil 134 is used in the refrigerant 107 or not used in the refrigerant 107, in configurations where the oil recovery tube 268 is used or not used, in configurations where the heat exchanger 116 is used or not used, or combinations thereof.

In the second aspect, an accumulator 102 is disclosed. The same element numbers are used for the same or substantially the same components, and include the same or substantially the same function, and variations thereof, as described above and throughout the FIGS.

Referring to the FIG. 5 example of the second aspect, the accumulator 102 includes a housing 130 defining a housing cavity 132 configured to store a refrigerant 107. The accumulator 102 includes a low pressure refrigerant inlet line 128 in communication with the housing cavity 132 and a first low pressure refrigerant outlet line 138 in communication with the housing cavity 132. A second low pressure refrigerant outlet line 140 includes an inlet end 242 positioned in the housing cavity 132 in communication with the refrigerant in a liquid phase 112. The second low pressure refrigerant outlet line 140 is configured to transfer the refrigerant in the liquid phase 112 from the housing 130 to an evaporator 144. The vortex breaker 276 ispositioned in the housing cavity 132 and is configured to prevent entrainment of the refrigerant in a gaseous phase 110 into the second low pressure refrigerant outlet line 140 as described above.

In one example of the second aspect best seen in FIG. 3, the vortex breaker 276 includes a support 378 connected to the inlet end 242 of the second low pressure refrigerant outlet line 140. A plate 379 is connected to the support 378. The support 378 and the plate 379 defining an opening 380 in communication with the second low pressure refrigerant outlet line 140 and configured to allow passage of the refrigerant in the liquid phase 112 into the second low pressure refrigerant outlet line 140.

In one example of the vortex breaker 276, the support further includes legs 381 each connected to the plate 379 and the second low pressure refrigerant outlet line 140. The legs 381 and the plate 379 defining liquid refrigerant openings 380A in communication with the second low pressure refrigerant outlet line 140. The liquid refrigerant openings 380A are configured to allow passage of the refrigerant in the liquid phase 112 into the second low pressure refrigerant outlet line 140.

In one example of the vortex breaker 276, the sidewall 384 is connected to the support 378 or the plate 379, or a combination thereof. The sidewall 384 is positioned in the opening 380 and is configured to prevent entrainment of the refrigerant in the gaseous phase 110 into the second low pressure refrigerant outlet line 140. In one example, the sidewall 384 is removably connected to the support 378 or the plate 379, or a combination thereof. Alternate or additional structures, for example membranes, filters, or other devices described above may be used in the second aspect.

In one example of the second aspect, the accumulator 102 further includes a separator container 133 positioned in the housing cavity 132 and includes a bottom portion 260, a top portion 262 and defines a separator container cavity 263. The separator container 133 is configured to store and promote separation of the refrigerant in the gaseous phase 110 and the refrigerant in the liquid phase 112 in the separation container cavity 263. The refrigerant in the gaseous phase 110 is positioned or rises toward the top portion 262 of the separator container 133 above the refrigerant in the liquid phase 112 as described above.

In one example of the second aspect, the separator container 133 of the accumulator 102 is configured to store and promote the separation of oil 134 from the refrigerant in the gaseous phase 110 and the refrigerant in the liquid phase 112. The oil is positioned or settles toward the bottom portion of the separator container 133 below the refrigerant in the liquid phase 112 as described above.

In one example of the second aspect, the accumulator 102 includes an oil recovery tube 268 positioned in the separator container cavity 263 and connected to the separator container 133. The oil recovery tube 268 includes an inlet end 269 positioned in the separator container cavity 263 in communication with the refrigerant in the gaseous phase 110. The oil recovery tube includes a lower portion 270 positioned in the oil 134. The oil recovery tube 268 includes an outlet end 271 positioned exterior to the separator container 133 in the housing cavity 132. An oil recovery orifice 272 is positioned at the lower portion 270 of the oil recovery tube 268 in communication with the oil 134. The oil recovery tube 268 is configured to transfer the refrigerant in the gaseous phase 110 from the separator container 133 and the oil 134 received through the oil recovery orifice 272 to the housing cavity 132 for further transfer through the first low pressure refrigerant outlet line 138 to the compressor 104 as described above.

In one example of the second aspect best seen in FIGS. 1 and 2, the accumulator 102 includes a high pressure refrigerant inlet line 114 and a high pressure refrigerant outlet line 118. The accumulator 102 further includes an internal heat exchanger 116 positioned in the housing cavity 132 in communication with the high pressure refrigerant inlet line 114 and the high pressure refrigerant outlet line 118. The internal heat exchanger 116 is configured to expel heat 274 to the housing cavity 132.

In a third aspect best seen in FIGS. 1 and 2, a thermal cycle system 100 is disclosed. The same element numbers are used for the same or substantially the same components, and include the same or substantially the same function, and variations thereof, as described above and throughout the FIGS. The thermal cycle system 100 in the third aspect includes the accumulator 102 including the internal heat exchanger 116, the compressor 104, the gas cooler 108, the ejector 122, and the evaporator 144. In one example of the third aspect, the accumulator 102 includes the vortex breaker 276. It is understood that the thermal cycle system 100 can be implemented without the ejector 122. It is understood that the ejector 122 can be used in any variations or configurations of the thermal cycle system 100 described herein. It is understood that the ejector 122 can be used in combination with the separator container 133 or where the separator container 133 is not used, in configurations where oil 134 is used in the refrigerant 107 or not used, in configurations where the oil recovery tube 268 is used or not used, in configurations where the heat exchanger 116 is used or not used, or combinations thereof.

In the aspects and examples of the thermal cycle system 100 described above, a control system 148 can be used to monitor and control one or more aspects or components of the thermal cycle system 100 or the accumulator 102. The control system 148 may be a dedicated or stand-alone system for monitoring or controlling the thermal cycle system 100 or the accumulator 102, or may be part of or integrated into a central control system, for example a central vehicle control system. The control system 148 may communicate electronically with one or more components through hardwire connections or wirelessly through protocols known by persons skilled in the art.

In one example, the control system 148 includes sensors at predetermined points in the thermal cycle system 100 or the accumulator 102 to monitor predetermined conditions or metrics, for example temperature, pressure, or material volume flow, or combinations thereof. The control system 148 may include one or more controlled components, for example the compressor 104, the ejector 122, the valve 146 and other components described herein. The control system 148 may also include a computer processor, a memory storage unit, a communications interface, and a bus to connect the components of control system 148. Additional or alternate components may be used for the control system 148 to suit the particular application and performance requirements.

The thermal cycles system and the accumulator described above may be implemented in the context of a system that includes the gathering and use of data available from various sources. As an example, such data may identify the user and include user-specific settings or preferences. The present disclosure contemplates that in some instances, this gathered data may include personal information data that uniquely identifies or can be used to contact or locate a specific person. Such personal information data can include demographic data, location-based data, telephone numbers, email addresses, twitter ID's, home addresses, data or records relating to a user's health or level of fitness (e.g., vital signs measurements, medication information, exercise information), date of birth, or any other identifying or personal information.

The present disclosure recognizes that the use of such personal information data, in the present technology, can be used to the benefit of users. For example, a user profile may be established that stores climate control preferences for a transportation vehicle compartment. Accordingly, use of such personal information data enhances the user's experience.

The present disclosure contemplates that the entities responsible for the collection, analysis, disclosure, transfer, storage, or other use of such personal information data will comply with well-established privacy policies and/or privacy practices. In particular, such entities should implement and consistently use privacy policies and practices that are generally recognized as meeting or exceeding industry or governmental requirements for maintaining personal information data private and secure. Such policies should be easily accessible by users, and should be updated as the collection and/or use of data changes. Personal information from users should be collected for legitimate and reasonable uses of the entity and not shared or sold outside of those legitimate uses. Further, such collection/sharing should occur after receiving the informed consent of the users. Additionally, such entities should consider taking any needed steps for safeguarding and securing access to such personal information data and ensuring that others with access to the personal information data adhere to their privacy policies and procedures. Further, such entities can subject themselves to evaluation by third parties to certify their adherence to widely accepted privacy policies and practices. In addition, policies and practices should be adapted for the particular types of personal information data being collected and/or accessed and adapted to applicable laws and standards, including jurisdiction-specific considerations. For instance, in the US, collection of or access to certain health data may be governed by federal and/or state laws, such as the Health Insurance Portability and Accountability Act (HIPAA); whereas health data in other countries may be subject to other regulations and policies and should be handled accordingly. Hence different privacy practices should be maintained for different personal data types in each country.

Despite the foregoing, the present disclosure also contemplates embodiments in which users selectively block the use of, or access to, personal information data. That is, the present disclosure contemplates that hardware and/or software elements can be provided to prevent or block access to such personal information data. For example, in the case of storing a user profile for climate control of a transportation vehicle passenger compartment, the present technology can be configured to allow users to select to “opt in” or “opt out” of participation in the collection of personal information data during registration for services or anytime thereafter. In another example, users can select not to provide data regarding usage of specific applications. In yet another example, users can select to limit the length of time that application usage data is maintained or entirely prohibit the development of an application usage profile. In addition to providing “opt in” and “opt out” options, the present disclosure contemplates providing notifications relating to the access or use of personal information. For instance, a user may be notified upon downloading an app that their personal information data will be accessed and then reminded again just before personal information data is accessed by the app.

Moreover, it is the intent of the present disclosure that personal information data should be managed and handled in a way to minimize risks of unintentional or unauthorized access or use. Risk can be minimized by limiting the collection of data and deleting data once it is no longer needed. In addition, and when applicable, including in certain health related applications, data de-identification can be used to protect a user's privacy. De-identification may be facilitated, when appropriate, by removing specific identifiers (e.g., date of birth, etc.), controlling the amount or specificity of data stored (e.g., collecting location data at a city level rather than at an address level), controlling how data is stored (e.g., aggregating data across users), and/or other methods.

Therefore, although the present disclosure broadly covers use of personal information data to implement one or more various disclosed embodiments, the present disclosure also contemplates that the various embodiments can also be implemented without the need for accessing such personal information data. That is, the various embodiments of the present technology are not rendered inoperable due to the lack of all or a portion of such personal information data. For example, information needed for the control of the thermal cycle system for passenger compartment climate control may be determined each time the thermal cycle system is used without subsequently storing the information or associating with the particular user.

Claims

1. A thermal cycle system, comprising: a high pressure refrigerant inlet line;a high pressure refrigerant outlet line;an accumulator including a housing defining a housing cavity configured to store a refrigerant;a low pressure refrigerant inlet line in communication with the housing cavity;a first low pressure refrigerant outlet line in communication with the housing cavity;a second low pressure refrigerant outlet line includes an inlet end positioned in the housing cavity in communication with the refrigerant, the second low pressure refrigerant outlet line is configured to transfer the refrigerant in a liquid phase from the accumulator to an evaporator; andan internal heat exchanger is positioned in the housing cavity in communication with the high pressure refrigerant inlet line and the high pressure refrigerant outlet line and is configured to expel heat to the housing cavity.

2. The thermal cycle system of claim 1, wherein the accumulator further comprises: a separator container positioned in the housing cavity including a bottom portion, a top portion and defining a separator container cavity, the separator container is configured to store and promote separation of the refrigerant in a gaseous phase and the refrigerant in the liquid phase in the separator container cavity, the refrigerant in the gaseous phase is positioned toward the top portion of the separator container above the refrigerant in the liquid phase.

3. The thermal cycle system of claim 2, wherein the low pressure refrigerant inlet line is configured to transfer the refrigerant into the separator container cavity.

4. The thermal cycle system of claim 2, wherein the separator container is configured to further store and promote separation of oil from the refrigerant in the gaseous phase and the refrigerant in the liquid phase, the oil positioned toward the bottom portion of the separator container below the refrigerant in the liquid phase.

5. The thermal cycle system of claim 4, wherein the accumulator further comprises: an oil recovery tube positioned in the separator container cavity, the oil recovery tube comprising: an inlet end positioned in the separator container cavity in communication with the refrigerant in the gaseous phase;a lower portion positioned in the oil;an outlet end positioned exterior to the separator container in the housing cavity; andan oil recovery orifice positioned at the lower portion of the oil recovery tube and in communication with the oil, the oil recovery tube configured to transfer the refrigerant in the gaseous phase from the separator container and the oil received through the oil recovery orifice to the housing cavity for further transfer through the first low pressure refrigerant outlet line to a compressor.

6. The thermal cycle system of claim 5, wherein the high pressure refrigerant inlet line is configured to transfer refrigerant in the liquid phase or refrigerant in the gaseous phase, or combinations thereof, under high pressure and high temperature to the internal heat exchanger, the internal heat exchanger is configured to expel heat into the housing cavity to elevate a temperature of the refrigerant in the gaseous phase, the refrigerant in the liquid phase, or the oil, or combinations thereof, positioned in the housing cavity.

7. The thermal cycle system of claim 1, wherein the high pressure refrigerant inlet line is configured to transfer the refrigerant in the liquid phase, the refrigerant in a gaseous phase, or combinations thereof, under high pressure and high temperature to the internal heat exchanger, the internal heat exchanger is configured to expel heat to the housing cavity.

8. The thermal cycle system of claim 1, further comprising: a vortex breaker positioned in the housing cavity and is configured to prevent entrainment of the refrigerant in a gaseous phase into the second low pressure refrigerant outlet line.

9. The thermal cycle system of claim 8, wherein the vortex breaker further comprises: a support connected to the inlet end of the second low pressure refrigerant outlet line; anda plate connected to the support, the support and the plate defining an opening in communication with the second low pressure refrigerant outlet line configured to allow passage of the refrigerant in the liquid phase into the second low pressure refrigerant outlet line.

10. The thermal cycle system of claim 9, wherein the support further comprises legs each connected to the plate and the second low pressure refrigerant outlet line, the legs and the plate together defining liquid refrigerant openings in communication with the second low pressure refrigerant outlet line configured to allow passage of the refrigerant in the liquid phase into the second low pressure refrigerant outlet line.

11. The thermal cycle system of claim 9, wherein the vortex breaker further comprises: a sidewall connected to the support or the plate, or a combination thereof, and positioned in the opening, the sidewall is configured to prevent entrainment of the refrigerant in the gaseous phase into the second low pressure refrigerant outlet line.

12. The thermal cycle system of claim 11, wherein the sidewall is removably connected to the support or the plate, or a combination thereof.

13. The thermal cycle system of claim 1, wherein the first low pressure refrigerant outlet line is in communication with a compressor and is configured to transfer refrigerant in a gaseous phase from the accumulator to the compressor.

14. An accumulator, comprising: a housing defining a housing cavity configured to store a refrigerant;a low pressure refrigerant inlet line in communication with the housing cavity;a first low pressure refrigerant outlet line in communication with the housing cavity;a second low pressure refrigerant outlet line includes an inlet end positioned in the housing cavity in communication with the refrigerant in a liquid phase, the second low pressure refrigerant outlet line is configured to transfer the refrigerant in the liquid phase from the housing to an evaporator; anda vortex breaker is positioned in the housing cavity and is configured to prevent entrainment of the refrigerant in a gaseous phase into the second low pressure refrigerant outlet line.

15. The accumulator of claim 14, wherein the vortex breaker further comprises: a support connected to the inlet end of the second low pressure refrigerant outlet line; anda plate connected to the support, the support and the plate defining an opening in communication with the second low pressure refrigerant outlet line configured to allow passage of the refrigerant in the liquid phase into the second low pressure refrigerant outlet line.

16. The accumulator of claim 15, wherein the support further comprises legs each connected to the plate and the second low pressure refrigerant outlet line, the legs and the plate together defining liquid refrigerant openings in communication with the second low pressure refrigerant outlet line configured to allow passage of the refrigerant in the liquid phase into the second low pressure refrigerant outlet line.

17. The accumulator of claim 15, wherein the vortex breaker further comprises: a sidewall connected to the support or the plate, or a combination thereof, and positioned in the opening, the sidewall configured to prevent entrainment of the refrigerant in the gaseous phase into the second low pressure refrigerant outlet line.

18. The accumulator of claim 17, wherein the sidewall is removably connected to the support or the plate, or a combination thereof.

19. The accumulator of claim 14, further comprising: a separator container positioned in the housing cavity including a bottom portion, a top portion and defining a separator container cavity, the separator container is configured to store and promote separation of the refrigerant in the gaseous phase and the refrigerant in the liquid phase in the separation container cavity, the refrigerant in the gaseous phase is positioned toward the top portion of the separator container above the refrigerant in the liquid phase.

20. The accumulator of claim 19, wherein the separator container is configured to further store and promote separation of oil from the refrigerant in the gaseous phase and the refrigerant in the liquid phase, the oil positioned toward the bottom portion of the separator container below the refrigerant in the liquid phase.

21. The accumulator of claim 20, further comprising: an oil recovery tube positioned in the separator container cavity, the oil recovery tube comprising: an inlet end positioned in the separator container cavity in communication with the refrigerant in the gaseous phase;a lower portion positioned in the oil;an outlet end positioned exterior to the separator container in the housing cavity; andan oil recovery orifice positioned at the lower portion of the oil recovery tube and in communication with the oil, the oil recovery tube configured to transfer the refrigerant in the gaseous phase from the separator container and oil received through the oil recovery orifice to the housing cavity for further transfer through the first low pressure refrigerant outlet line to a compressor.

22. The accumulator of claim 14, further comprising: a high pressure refrigerant inlet line;a high pressure refrigerant outlet line; andan internal heat exchanger is positioned in the housing cavity in communication with the high pressure refrigerant inlet line and the high pressure refrigerant outlet line, the internal heat exchanger is configured to expel heat to the housing cavity.

23. The accumulator of claim 14, wherein the first low pressure refrigerant outlet line is in communication with a compressor and is configured to transfer the refrigerant in the gaseous phase from the housing to the compressor.

24. A thermal cycle system, comprising: a compressor configured to transfer a refrigerant under pressure;a gas cooler in communication with the compressor;an accumulator in communication with the gas cooler, the accumulator comprising: a housing defining a housing cavity configured to store the refrigerant;an internal heat exchanger positioned in the housing cavity in communication with the gas cooler and configured to expel heat from the refrigerant received from the gas cooler to the housing cavity;a first low pressure refrigerant outlet line; anda second low pressure refrigerant outlet line including an inlet end positioned in the housing cavity in communication with the refrigerant in a liquid phase;an ejector in communication with the internal heat exchanger and configured to lower a pressure and a temperature of the refrigerant received from the internal heat exchanger, the ejector including an ejector outlet line in communication with the housing cavity of the accumulator;an evaporator in communication with the second low pressure refrigerant outlet line and configured to receive the refrigerant in the liquid phase through the second low pressure refrigerant outlet line, the evaporator in communication with the ejector; anda valve positioned in the second low pressure refrigerant outlet line upstream of the evaporator, the valve configured to meter a flow of the refrigerant in the liquid phase to the evaporator.

25. The thermal cycle system of claim 24, further comprising: a vortex breaker positioned in the housing cavity configured to prevent entrainment of the refrigerant in a gaseous phase into the second low pressure refrigerant outlet line.