Heat dissipation components for linear compressors

Abstract

A linear compressor includes a housing defining an oil pan for collecting lubricant, and a pump for circulating the lubricant within the housing. A heat dissipation or heat exchange assembly includes a plate mounted on a lower portion of the housing to define one or more fluid passages between the plate and the housing. Hot oil is collected from working components of the linear compressor and passed through the one or more fluid passages to dissipate heat through the housing before returning to the oil pan.

Description

Technical Field

[0001] The present invention relates to a linear compressor, and in particular to a heat dissipation system for a linear compressor. Background Art

[0002] Some refrigeration appliances include a sealed system for cooling the refrigeration compartment of the appliance. These sealed systems typically include a compressor that produces compressed refrigerant during operation. This compressed refrigerant flows to an evaporator, where heat is exchanged between the refrigerant and the refrigeration compartment, cooling the refrigeration compartment and the food products therein. More recently, some refrigeration appliances include a linear compressor for compressing the refrigerant. Linear compressors typically include a piston and a drive coil. The drive coil generates a force that causes the piston to slide forward and backward within the compartment. As the piston moves within the compartment, it compresses the refrigerant.

[0003] The compressor housing typically includes an oil or lubricant supply system to lubricate the pistons and reduce friction losses caused by the pistons rubbing against the chamber walls, which can negatively impact the efficiency of the associated refrigeration appliance. However, such linear compressors often experience performance issues when the oil temperature is high. For example, when the oil heats during compressor operation, it can atomize or otherwise splash around, which can cause mechanical losses in the springs or reliability issues related to oil droplets being entrained into the suction port. Some linear compressors include external heat exchangers that pass the hot oil outside the housing, but these heat exchangers are complex, costly, and prone to leaks.

[0004] Therefore, there is a need for a linear compressor having features that improve performance. More particularly, a linear compressor having an improved system for dissipating heat from the oil would be particularly beneficial. Summary of the Invention

[0005] Various aspects and advantages of the present invention will be set forth in part in the following description, or may be obvious from the description, or may be learned through practice of the present invention.

[0006] In one exemplary aspect of the present disclosure, a linear compressor defining an axial direction and a vertical direction is provided. The linear compressor includes: a housing defining an oil pan for collecting lubricant; a pump for circulating the lubricant within the housing, the pump including a pump inlet located within the oil pan; and a heat sink assembly, the heat sink assembly including: a plate mounted to an inner surface of the housing; and a fluid passage defined between the plate and the inner surface of the housing, the fluid passage having a fluid inlet for receiving the lubricant and a fluid outlet for draining the lubricant back into the oil pan.

[0007] In another exemplary aspect of the present disclosure, a heat dissipation assembly for a linear compressor is provided. The linear compressor includes a housing defining an oil pan for collecting lubricant; the heat dissipation assembly includes a plate mounted to an inner surface of the housing; and a fluid passage defined between the plate and the inner surface of the housing, the fluid passage having a fluid inlet for receiving lubricant and a fluid outlet for draining the lubricant back into the oil pan.

[0008] The above and other features, aspects and advantages of the present invention will be better understood with reference to the following description.The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments of the present invention and, together with the description, serve to explain the principles of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0009] A full and enabling disclosure of the invention, including the best mode thereof, is set forth in the specification with reference to the accompanying drawings to those skilled in the art.

[0010] Figure 1 is a front perspective view of a refrigeration appliance according to an exemplary embodiment of the present invention.

[0011] Figure 2 yes Figure 1 Schematic diagram of certain components of an exemplary refrigeration appliance.

[0012] Figure 3 is a cross-sectional perspective view of a linear compressor according to an exemplary embodiment of the present invention.

[0013] Figure 4 yes Figure 3 FIG. 1 is another cross-sectional perspective view of an exemplary linear compressor according to an exemplary embodiment of the present invention.

[0014] Figure 5 is a perspective view of a linear compressor according to an exemplary embodiment of the present invention, with the compressor removed for clarity.

[0015] Figure 6 yes Figure 3 FIG. 2 is a cross-sectional view of an exemplary linear compressor according to an exemplary embodiment of the present invention, wherein the piston is in an extended position.

[0016] Figure 7 yes Figure 3 FIG. 1 is a cross-sectional view of an exemplary linear compressor according to an exemplary embodiment of the present invention, wherein the piston is in a retracted position.

[0017] Figure 8 yes Figure 3 FIG. 1 is a schematic cross-sectional view of an exemplary linear compressor including a heat sink assembly according to an exemplary embodiment of the present invention.

[0018] Figure 9 Provided Figure 8 FIG. 1 is a perspective view of a plate of an exemplary heat dissipation assembly according to an exemplary embodiment of the present invention.

[0019] Figure 10 Provided Figure 8 FIG. 1 is a cross-sectional view of a plate of an exemplary heat dissipation assembly according to an exemplary embodiment of the present invention, wherein the plate is mounted to a housing.

[0020] Repeat use of reference characters in the present specification and drawings is intended to represent same or analogous features or elements of the invention. DETAILED DESCRIPTION

[0021] While embodiments of the present invention will be described in detail, one or more examples of these embodiments are illustrated in the accompanying drawings. Each example is provided for the purpose of illustrating the present invention and is not intended to limit the present invention. Indeed, it will be apparent to those skilled in the art that various modifications and variations may be made to the present invention without departing from the scope or spirit of the invention. For example, features shown or described as part of one embodiment may be used in combination with another embodiment to form additional embodiments. Therefore, the present invention is intended to cover such modifications and variations as fall within the scope of the present invention and its equivalents.

[0022] Figure 1 A refrigeration appliance 10 is depicted, comprising Figure 2 1. A sealed refrigeration system 60 is shown. It should be understood that the term "refrigeration appliance" is used herein in a generic sense to encompass any type of refrigeration appliance, such as a freezer, a refrigerator / freezer combination, and any make or model of conventional refrigerator. Furthermore, it should be understood that the present invention is not limited to use in appliances. Thus, the present invention may be used for any other suitable purpose, such as vapor compression within an air conditioning unit or air compression within an air compressor.

[0023] exist Figure 1 In the exemplary embodiment shown, refrigeration appliance 10 is depicted as an upright refrigerator having a cabinet or housing 12 that defines a number of internal refrigerated storage compartments. Specifically, refrigeration appliance 10 includes an upper fresh food compartment 14 having a door 16 and a lower freezer compartment 18 having an upper drawer 20 and a lower drawer 22. Drawers 20 and 22 are "pull-out" drawers because they can be manually moved into and out of freezer compartment 18 on a suitable sliding mechanism.

[0024] Figure 2FIG2 is a schematic diagram of certain components of refrigeration appliance 10, including its sealed refrigeration system 60. A mechanical compartment 62 contains the components used to perform a vapor compression cycle to cool air. These components include a compressor 64, a condenser 66, an expansion device 68, and an evaporator 70, all connected in series and filled with refrigerant. As will be understood by those skilled in the art, refrigeration system 60 may include additional components, such as at least one additional evaporator, compressor, expansion device, and / or condenser. As an example, refrigeration system 60 may include two evaporators.

[0025] Within refrigeration system 60, refrigerant flows into compressor 64, which operates to increase the pressure of the refrigerant. This compression of the refrigerant causes its temperature to increase, which decreases as the refrigerant passes through condenser 66. Within condenser 66, heat exchange with the surrounding air occurs to cool the refrigerant. As indicated by arrows AC, a fan 72 is used to draw air through condenser 66 to provide forced convection, thereby achieving faster and more efficient heat exchange between the refrigerant within condenser 66 and the surrounding air. Therefore, as will be appreciated by those skilled in the art, increasing the air flow through condenser 66 can improve the efficiency of condenser 66, for example, by improving the cooling of the refrigerant contained therein.

[0026] An expansion device 68 (e.g., a valve, capillary tube, or other restriction) receives refrigerant from the condenser 66. From the expansion device 68, the refrigerant enters the evaporator 70. As the refrigerant leaves the expansion device 68 and enters the evaporator 70, its pressure decreases. Due to the pressure drop and phase change in the refrigerant, the evaporator 70 is at a lower temperature than the chambers 14 and 18 of the refrigeration appliance 10. This produces cooled air, which cools the chambers 14 and 18 of the refrigeration appliance 10. Therefore, the evaporator 70 is a type of heat exchanger that transfers heat from the air passing through the evaporator 70 to the refrigerant flowing through the evaporator 70.

[0027] Collectively, the vapor compression cycle components, associated fans, and associated chambers in the refrigeration circuit are sometimes referred to as a sealed refrigeration system, which is operable to force cool air through the compartments 14, 18 ( Figure 1 ). Figure 2 The refrigeration system 60 depicted in FIG. 5 is provided as an example only. Therefore, other configurations for using a refrigeration system are also within the scope of the present invention.

[0028] Go to Figures 3 to 7 , the linear compressor 100 will be described according to an exemplary embodiment of the present invention. Specifically, Figure 3 and Figure 4 A cross-sectional perspective view of a linear compressor 100 is provided; Figure 5 A perspective view of a linear compressor 100 is provided with the compressor housing or casing 102 removed for clarity; Figure 6 and Figure 7 Cross-sectional views of a linear compressor are provided with the piston in an extended position and a retracted position, respectively. It should be understood that linear compressor 100 is used herein merely as an exemplary embodiment to illustrate various aspects of the present invention. Modifications and variations may be made to linear compressor 100 without departing from the scope of the present invention.

[0029] like Figure 3 and Figure 4 As shown in the example of FIG, housing 102 may include a lower or lower housing portion 104 and an upper or upper housing portion 106, which, when combined, form a substantially enclosed cavity 108 for housing the various components of linear compressor 100. Specifically, for example, cavity 108 may be a sealed or airtight enclosure that houses the working components of linear compressor 100 and may hinder or prevent refrigerant from leaking or escaping from refrigeration system 60. Furthermore, linear compressor 100 generally defines an axial direction A, a radial direction R, and a circumferential direction C. It should be understood that the linear compressor 100 described and illustrated herein is merely illustrative of various aspects of the present invention. Modifications and variations may be made to linear compressor 100 without departing from the scope of the present invention.

[0030] Go to Figures 3 to 7 , the various parts and working components of the linear compressor 100 will be described according to an exemplary embodiment. As shown, the linear compressor 100 includes a housing 110 that extends between a first end 112 and a second end 114 along an axial direction A. The housing 110 includes a cylinder 117 that defines a chamber 118. The cylinder 117 is located at or near the first end 112 of the housing 110. The chamber 118 extends longitudinally along the axial direction A. As discussed in more detail below, the linear compressor 100 can be operated to increase the fluid pressure within the chamber 118 of the linear compressor 100. The linear compressor 100 can be used to compress any suitable fluid, such as a refrigerant or air. In particular, the linear compressor 100 can be used in refrigeration appliances, such as refrigeration appliance 10 ( Figure 1 ), in the refrigeration appliance 10, the linear compressor 100 can be used as the compressor 64 ( Figure 2 ).

[0031] The linear compressor 100 includes a stator 120 of an electric motor mounted or fixed to the housing 110. For example, the stator 120 generally includes an outer back iron 122 and a drive coil 124, both of which extend around the circumference C within the housing 110. The linear compressor 100 also includes one or more valves that permit refrigerant to enter and exit the chamber 118 during operation of the linear compressor 100. For example, a discharge muffler 126 is located at the end of the chamber 118 for regulating the flow of refrigerant out of the chamber 118, while a suction valve 128 (shown only for clarity) is provided. Figures 6 and 7) regulates the flow of refrigerant into compartment 118.

[0032] The piston 130 has a piston head 132 and is slidably received in the chamber 118 of the cylinder 117. Specifically, the piston 130 can move along the axial direction A. While the piston head 132 slides in the chamber 118, the piston head 132 compresses the refrigerant in the chamber 118. As an example, starting from the top dead center position (e.g., see Figure 6 ), the piston head 132 can slide in the chamber 118 along the axial direction A toward the bottom dead center position (for example, see Figure 7 ), i.e., the expansion stroke of piston head 132. When piston head 132 reaches the bottom dead center position, piston head 132 changes direction and slides back within chamber 118 toward the top dead center position, i.e., the compression stroke of piston head 132. It should be understood that linear compressor 100 may include additional piston heads and / or additional chambers at opposite ends of linear compressor 100. Therefore, in alternative exemplary embodiments, linear compressor 100 may have multiple piston heads.

[0033] As shown, the linear compressor 100 further includes a mover 140, which is generally driven by the stator 120 to compress the refrigerant. Specifically, for example, the mover 140 may include an inner back iron 142 located within the stator 120 of the motor. Specifically, the outer back iron 122 and / or the drive coil 124 may extend around the inner back iron 142, for example, along a circumferential direction C. The inner back iron 142 further includes an outer surface facing the outer back iron 122 and / or the drive coil 124. For example, at least one drive magnet 144 is mounted to the inner back iron 142 at its outer surface 137.

[0034] The drive magnet 144 can face and / or be exposed to the drive coil 124. In particular, the drive magnet 144 can be separated from the drive coil 124 by an air gap, for example, by an air gap along the radial direction R. Thus, an air gap can be defined between the opposing surfaces of the drive magnet 144 and the drive coil 124. The drive magnet 144 can also be mounted or fixed to the inner back iron 142 so that the outer surface of the drive magnet 144 is substantially flush with the outer surface of the inner back iron 142. Thus, the drive magnet 144 can be embedded within the inner back iron 142. In this way, during operation of the linear compressor 100, the magnetic field from the drive coil 124 may have to pass through only a single air gap between the outer back iron 122 and the inner back iron 142. The linear compressor 100 may be more efficient relative to a linear compressor having air gaps on both sides of the drive magnet.

[0035] like Figure 3As shown in FIG, the drive coil 124 extends around the inner back iron 142, for example, along a circumferential direction C. In an alternative exemplary embodiment, the inner back iron 142 may extend around the drive coil 124 along a circumferential direction C. The drive coil 124 is operable to cause the inner back iron 142 to move along an axial direction A during operation of the drive coil 124. For example, a current source (not shown) may be used to induce a current within the drive coil 124 to generate a magnetic field that engages the drive magnet 144 and causes the piston 130 to move along the axial direction A, thereby compressing the refrigerant within the chamber 118, as described above and as will be understood by those skilled in the art. In particular, the magnetic field of the drive coil 124 may engage the drive magnet 144 to cause the inner back iron 142 and the piston head 132 to move along the axial direction A during operation of the drive coil 124. Thus, by causing the inner back iron 142 to move along the axial direction A during operation of the drive coil 124, the drive coil 124 may cause the piston 130 to slide between a top dead center position and a bottom dead center position.

[0036] The linear compressor 100 may include various components for permitting and / or regulating the operation of the linear compressor 100. In particular, the linear compressor 100 includes a controller (not shown) configured to regulate the operation of the linear compressor 100. The controller may be in operative communication with, for example, the electric motor (e.g., the drive coil 124 of the electric motor). Thus, by inducing a current in the drive coil 124, the controller may selectively activate the drive coil 124 to compress the refrigerant using the piston 130 as described above.

[0037] The controller includes memory and one or more processors, such as a microprocessor or CPU, which can be general-purpose or specialized microprocessors operable to execute programmed instructions or microcontrol code associated with the operation of the linear compressor 100. The memory can be random access memory, such as DRAM, or read-only memory, such as ROM or FLASH. The processor executes the programmed instructions stored in the memory. The memory can be a separate component from the processor or can be included onboard the processor. Alternatively, the controller can be configured to perform control functions without using a microprocessor, for example, using a combination of discrete analog and / or digital logic circuits (such as switches, amplifiers, integrators, comparators, flip-flops, and AND gates) instead of relying on software.

[0038] The inner back iron 142 further includes an outer cylinder 146 and an inner sleeve 148. The outer cylinder 146 defines the outer surface of the inner back iron 142 and has an inner surface disposed opposite the outer surface of the outer cylinder 146. The inner sleeve 148 is located on or at the inner surface of the outer cylinder 146. A first interference fit between the outer cylinder 146 and the inner sleeve 148 can couple or secure the outer cylinder 146 and the inner sleeve 148 together. In alternative exemplary embodiments, the inner sleeve 148 can be welded, glued, fastened, or connected to the outer cylinder 146 via any other suitable mechanism or method.

[0039] The outer cylinder 146 can be constructed from or using any suitable material. For example, the outer cylinder 146 can be constructed from or using a plurality of (e.g., ferromagnetic) laminations. These laminations are arranged along a circumferential direction C to form the outer cylinder 146 and are mounted or secured to each other using rings pressed against the ends of the laminations. The outer cylinder 146 can define a recess extending inwardly from the outer surface of the outer cylinder 146 along a radial direction R. The drive magnet 144 is located in the recess on the outer cylinder 146, for example, so that the drive magnet 144 is embedded in the outer cylinder 146.

[0040] The linear compressor 100 also includes a pair of planar springs 150. Each planar spring 150 can be coupled to a respective end of the inner back iron 142, for example, along the axial direction A. During operation of the drive coil 124, the planar springs 150 support the inner back iron 142. Specifically, the inner back iron 142 is suspended within the stator or motor of the linear compressor 100 by the planar springs 150, such that movement of the inner back iron 142 along the radial direction R is hindered or restricted, while movement along the axial direction A is relatively unimpeded. Therefore, the stiffness of the planar springs 150 along the radial direction R can be substantially higher than that along the axial direction A. In this manner, during operation of the motor and during movement of the inner back iron 142 in the axial direction A, the planar springs 150 can help maintain a uniform air gap between the drive magnet 144 and the drive coil 124, for example, along the radial direction R. The planar springs 150 can also help prevent lateral pulling forces of the motor from being transmitted to the piston 130 and reacting as frictional losses in the cylinder 117.

[0041] The flexible base 160 is mounted to and extends through the inner back iron 142. Specifically, the flexible base 160 is mounted to the inner back iron 142 via the inner sleeve 148. Thus, the flexible base 160 can be coupled (e.g., threaded) to the inner sleeve 148 at the inner sleeve 148 and / or at an intermediate portion of the flexible base 160 to mount or secure the flexible base 160 to the inner sleeve 148. The flexible base 160 can also help form a coupling 162. The coupling 162 connects the inner back iron 142 and the piston 130, thereby transmitting movement of the inner back iron 142 (e.g., along the axial direction A) to the piston 130.

[0042] The coupling 162 may be a flexible coupling having flexibility or pliability along the radial direction R. In particular, the coupling 162 may be sufficiently flexible along the radial direction R so that little or no movement of the inner back iron 142 along the radial direction R is transmitted through the coupling 162 to the piston 130. In this manner, the lateral pulling force of the motor is decoupled from the piston 130 and / or the cylinder 117, and friction between the piston 130 and the cylinder 117 may be reduced.

[0043] As shown in the figures, the piston head 132 of the piston 130 has a piston cylindrical sidewall 170. The cylindrical sidewall 170 can extend from the piston head 132 toward the inner back iron 142 along the axial direction A. The outer surface of the cylindrical sidewall 170 can slide in the chamber 118 on the cylinder 117, and the inner surface of the cylindrical sidewall 170 can be disposed opposite the outer surface of the cylindrical sidewall 170. Therefore, the outer surface of the cylindrical sidewall 170 can face away from the center of the cylindrical sidewall 170 along the radial direction R, and the inner surface of the cylindrical sidewall 170 can face the center of the cylindrical sidewall 170 along the radial direction R.

[0044] Flexible base 160 extends between a first end 172 and a second end 174, for example, along an axial direction A. According to an exemplary embodiment, the inner surface of cylindrical sidewall 170 defines a ball seat 176 proximate the first end. Furthermore, coupling 162 also includes a ball head 178. Specifically, for example, ball head 178 is located at first end 172 of flexible base 160 and may contact flexible base 160 at first end 172 of flexible base 160. Furthermore, ball head 178 may contact piston 130 at ball seat 176 of piston 130. Specifically, ball head 178 may rest on ball seat 176 of piston 130 such that ball head 178 can slide and / or rotate on ball seat 176 of piston 130. For example, ball head 178 may have a truncated spherical surface positioned against ball seat 176 of piston 130, and the shape of ball seat 176 may be complementary to the truncated spherical surface of ball head 178. The frusto-spherical surface of the ball head 178 can slide and / or rotate on the ball seat 176 of the piston 130 .

[0045] For example, relative motion between the flexible mount 160 and the piston 130 at the interface between the ball head 178 and the ball seat 176 of the piston 130 can reduce friction between the piston 130 and the cylinder 117, compared to a fixed connection between the flexible mount 160 and the piston 130. For example, when the axis along which the piston 130 slides within the cylinder 117 is angled relative to the axis along which the internal back iron 142 reciprocates, the truncated spherical surface of the ball head 178 can slide on the ball seat 176 of the piston 130 to reduce friction between the piston 130 and the cylinder 117 relative to a rigid connection between the internal back iron 142 and the piston 130.

[0046] The flexible base 160 is connected to the inner back iron 142 distally from a first end 172 of the flexible base 160. For example, the flexible base 160 can be connected to the inner back iron 142 at a second end 174 of the flexible base 160 or between the first end 172 and the second end 174 of the flexible base 160. Instead, the flexible base 160 is located at or within the piston 130 at the first end 172 of the flexible base 160, as discussed in more detail below.

[0047] Additionally, the flexible base 160 includes a tubular wall 190 between the inner back iron 142 and the piston 130. A passage 192 within the tubular wall 190 is configured to direct a compressible fluid, such as refrigerant or air, through the flexible base 160 toward the piston head 132 and / or into the piston 130. The inner back iron 142 can be mounted to the flexible base 160 such that the inner back iron 142 extends around the tubular wall 190 in a central portion of the flexible base 160 between the first end 172 and the second end 174 of the flexible base 160. The passage 192 can extend within the tubular wall 190 between the first end 172 and the second end 174 of the flexible base 160, such that the compressible fluid can flow from the first end 172 of the flexible base 160 to the second end 174 of the flexible base 160 through the passage 192. In this manner, the compressible fluid can flow through the inner back iron 142 within the flexible base 160 during operation of the linear compressor 100. A muffler 194 may be located within the passage 192 within the tubular wall 190 to reduce noise from the compressible fluid flowing through the passage 192 .

[0048] The piston head 132 further defines at least one opening 196. The opening 196 of the piston head 132 extends through the piston head 132, for example, along the axial direction A. Thus, during operation of the linear compressor 100, fluid can flow through the piston head 132 via the opening 196 of the piston head 132 and into the chamber 118. In this manner, during operation of the linear compressor 100, fluid (i.e., fluid compressed by the piston head 132 within the chamber 118) can flow within the passage 192 through the flexible seat 160 and the internal back iron 142 to the piston 130. As explained above, the suction valve 128 ( Figures 6 and 7 ) may be located on piston head 132 to regulate the flow of compressible fluid into chamber 118 through opening 196 .

[0049] Still refer to Figures 3 to 7 Also refer to Figure 8 , a lubrication system 200 that can be used with the linear compressor 100 will be described. Specifically, the lubrication system 200 is configured to circulate a lubricant, such as oil, through the working or moving parts of the linear compressor 100 to reduce friction, improve efficiency, etc. Although the lubrication system 200 is described herein with respect to the linear compressor 100, it should be understood that aspects of the lubrication system 200 are applicable to any other suitable compressor or machine requiring continuous lubrication.

[0050] As shown, the housing 102 generally defines an oil pan 202 configured to collect oil (identified herein by reference numeral 204, see Figure 8 ). Specifically, an oil pan 202 is defined in the bottom of the lower housing 104. The lubrication system 200 further includes a pump 206 for continuously circulating the oil 204 through the components of the linear compressor 100 that require lubrication. In this regard, for example, the pump 206 includes a pump inlet 208 that is disposed near the bottom of the housing 102 within the oil pan 202. The pump 206 may be configured to pump oil 204 through a supply conduit 210 ( Figure 9 ) draws oil 204 from the oil pan 202 through a pump inlet 208. Although only one supply conduit 210 is shown for clarity, it should be understood that the lubrication system 200 may include any suitable number of supply conduits, nozzles, and other distribution features to provide oil 204 to various components throughout the linear compressor 100.

[0051] Obviously, according to the illustrated embodiment, the pump inlet 208 is located very close to and facing the bottom of the lower housing 104. In this way, the pump 206 can easily suck in the oil 204 even if the oil level is low. Specifically, the linear compressor 100 can be configured to accommodate the oil 204 that does not exceed the maximum oil filling line 212. For example, Figure 8A maximum oil fill line 212 is identified in FIG. , which may extend, for example, below halfway up the lower housing 104, below a quarter of the way up the lower housing 104, or even lower. During operation, the pump 206 circulates the oil 204 throughout the linear compressor 100, after which the oil 204 seeps or flows out of the working components and collects in the oil pan 202 before being recirculated. Although not shown here, it should be understood that the lubrication system 200 includes various features for treating, filtering, or conditioning the oil 204 during recirculation, such as various filters, screens, etc. Furthermore, it should be understood that while the pump 206 is shown as being located within the oil pan, the pump 206 may be located in any other location and may include a fluid path for drawing the oil 204 from the oil pan 202.

[0052] As also shown in the figures, the linear compressor 100 may include a suction port 220 for receiving a flow of refrigerant. Specifically, the suction port 220 may be defined on the housing 102, such as on the lower housing 104, and may be configured to receive a refrigerant supply conduit for providing refrigerant to the cavity 108. As explained above, the flexible base 160 includes a tubular wall 190 that defines a passage 192 for directing a compressible fluid, such as refrigerant gas, through the flexible base 160 toward the piston head 132. In this manner, the ideal flow path for the refrigerant gas is through the suction port 220, through the passage 192, through the opening 196, and into the chamber 118. The suction valve 128 may block the opening 196 during the compression stroke, while the discharge valve 116 may permit the compressed gas to exit the chamber 118 when the desired pressure is reached.

[0053] The flexible base 160 can further define a passage inlet 230, which is provided near the second end 174 of the flexible base 160, for gas to be sucked into the passage 192 from the suction port 220 or the cavity 108. Specifically, the passage inlet 230 can be an opening on the flexible base 160, which extends substantially in a vertical plane and opens towards the suction port 220. Specifically, according to the illustrated embodiment, the passage inlet 230 and the suction port 220 can be substantially located in the same horizontal plane. According to the illustrated embodiment, the suction port 220 and the passage inlet 230 are also provided near the midpoint of the housing 102 along the vertical direction V. However, it should be understood that, according to alternative embodiments, the suction port 220 and the passage inlet 230 can be positioned at any other suitable position in the housing 102.

[0054] Now specific reference Figures 8 to 10, linear compressor 100 may further include features for draining or dissipating heat that may have accumulated in oil or lubricant or elsewhere within linear compressor 100. Specifically, according to an exemplary embodiment, linear compressor 100 includes a heat sink assembly 240 that is positioned within cavity 108 and helps facilitate the discharge of heat energy from within cavity 108 to the exterior of housing 102. While an exemplary heat sink assembly 240 is described herein, it should be understood that changes and modifications may be made to heat sink assembly 240 without departing from the scope of the present invention.

[0055] According to the illustrated embodiment, the heat sink assembly 240 includes a plate 242 mounted to an inner surface 244 of the housing 102. Generally speaking, the plate 242 and the housing 102 collectively define one or more fluid passages 246. In this regard, the fluid passages 246 are at least partially defined by and between the plate 242 and the inner surface 244 of the housing 102. Each fluid passage 246 may include a fluid inlet 248 for receiving lubricant (as identified herein by reference numeral 204) and a fluid outlet 252 for draining the lubricant 204 back into the oil pan 202. To explain various aspects of the present invention, the heat sink assembly 240 will be described below as being used with the lubrication system 200 of the linear compressor 100. However, it should be understood that various aspects of the heat sink assembly 240 may be used with other compressors and other lubrication systems without departing from the scope of the present invention.

[0056] Generally speaking, the heat sink assembly 240 removes or discharges heat absorbed from the lubricant 204 during operation of the linear compressor 100. In this regard, for example, the heated lubricant 204 can be transferred directly from the moving components of the linear compressor 100 to the fluid inlet 248. In this regard, the heat sink assembly 240 can include any suitable mechanism, conduit, or other feature for collecting the lubricant 204 and directing it to the fluid inlet 248. For example, according to one exemplary embodiment, the heat sink assembly 240 can include a supply tube 254 that provides fluid communication between a hot oil collection point (e.g., generally identified herein by reference numeral 256) and the fluid inlet 248. For example, the hot oil collection point 256 can be an oil drain port 258 defined on the housing 110, through which the heated lubricant 204 is discharged. In this regard, the supply tube 254 can be a flexible tube having one end connected to an inlet boss 260 of the plate 242 defining the fluid inlet 248 and the other end connected to an oil drain 258 or another hot oil collection point 256. According to still other embodiments, the linear compressor 100 can include a collection pan or trough for collecting the lubricant 204 that has been heated during operation, and such a collection pan can direct the heated lubricant 204 directly into the supply tube 254 or the fluid inlet 248.

[0057] As the lubricant 204 passes through the fluid passage 246, thermal energy from the heated lubricant 204 can be transferred through the housing 102 to the surrounding environment. The fluid passage 246 can have any suitable size, shape, and configuration for maximizing heat transfer from the heated lubricant 204. For example, according to the illustrated embodiment, the fluid passage 246 is serpentine to increase the thermal contact area. According to still other embodiments, the fluid passage 246 can be curved, arched, wavy, zigzag, or any other suitable shape. Generally speaking, the fluid passage 246 flows downward so that gravity can help assist the lubricant 204 in flowing toward the fluid outlet 252. For example, according to the illustrated embodiment, the fluid inlet 242 is located at the top of the plate 242 along the vertical direction V, and the fluid outlet 252 is located at the bottom of the plate 242 along the vertical direction V, such as near the bottom of the oil pan 202. Specifically, according to the illustrated embodiment, the fluid outlet 252 is located directly above the maximum fill line 212, allowing the heated lubricant 204 to freely pass through the fluid outlet 252 to collect in the oil pan 202. Furthermore, while a single fluid passage 246 is shown, the heat sink assembly 240 may include any suitable number of fluid passages 246.

[0058] According to an exemplary embodiment, the plate 242 can be constructed from any material that is sufficiently rigid to maintain the fluid passage 246 containing the lubricant 204 therein. For example, the plate 242 can be formed by injection molding, for example, using a suitable plastic material such as injection molding grade polybutylene terephthalate (PBT), nylon 6, high impact polystyrene (HIPS), or acrylonitrile butadiene styrene (ABS). Alternatively, according to an exemplary embodiment, these components can be compression molded, for example, using sheet molding compound (SMC) thermoset plastic or other thermoplastic plastic. According to still other embodiments, the plate 242 can be constructed from metal or any other suitable rigid material, such as sheet metal.

[0059] Obviously, according to an exemplary embodiment, the plate 242 can have a lower thermal conductivity than the housing 102. In this manner, the plate 242 is generally a thermally insulating material, generally reducing the amount of heat transferred from the fluid passage 246 back into the cavity 108. Instead, the heat from the lubricant 204 tends to flow directly through the housing 102 to the surrounding environment. According to still other embodiments, such as Figure 10 As shown in , the plate 242 may include a thin stamped metal sheet 262 or may be otherwise constructed of relatively thin material. According to an exemplary embodiment, to improve the thermal resistance of the plate 242 including the metal sheet 262, the plate 242 may further include an insulating cover 264 located above the stamped metal sheet 262.

[0060] Additionally, according to exemplary embodiments, the plate 242 can define a plate thickness 270, and the housing 102 can define a housing thickness 272. According to exemplary embodiments, the plate thickness 270 can be greater than the housing thickness 272, for example, to improve the thermal insulation of the plate 242 relative to the housing 102 and increase the potential for heat to be removed through the housing 102. For example, according to exemplary embodiments, the plate thickness 270 is between approximately 1 and 5 times, between approximately 2 and 4 times, or approximately 3 times the housing thickness 272. Other suitable plate sizes, shapes, and configurations are possible within the scope of the present invention.

[0061] According to an exemplary embodiment, the plate 242 can be curved to match the contour of the inner surface 244 of the housing 102. In addition, it should be understood that the heat dissipation assembly 240 may include multiple plates 242, which are located at different locations within the housing 102 to dissipate heat at these locations. In addition, the size and position of the plate 242 can vary depending on the space constraints within the cavity 108. For example, the plate 242 can be thicker in areas with less space constraints. In addition, according to the illustrated embodiment, the plate 242 is mounted on the lower housing 104. In this way, the installation process of the supply tube 254 can be simplified. However, other suitable plate positions and configurations are possible within the scope of the present invention.

[0062] Obviously, the fluid passage 246 can be defined between the housing 102 and the plate 242 in any manner. Figure 8 and Figure 9 As shown in FIG, the plate 242 may define a plate recess 280 that defines a fluid passage 246. In contrast, as shown in FIG. Figure 10 As shown in FIG, the housing 102 may further define a housing groove 282 to define a portion of the fluid passage 246. It should be understood that the grooves 280 and 282 may be used together or alternatively. In fact, according to other embodiments, the fluid passage may be defined in any other suitable manner.

[0063] The plate 242 may be mounted to the housing 102 in any suitable manner. For example, according to an exemplary embodiment of the present invention, one or more mechanical fasteners may be used to mount the plate 242 to the housing 202. Figure 10 As shown in FIG, the mechanical fastener may include one or more studs 290 formed as part of the housing 102 or otherwise attached to the housing 102. One or more threaded nuts 292 may be configured to engage the studs 290 to secure the plate 242 to the housing 102. According to still other embodiments, the housing 102 may define a plurality of brackets that securely slide the plate 242 into a fixed position. In this regard, for example, the bracket may be an L-shaped bracket 294 (which is Figure 9), which extends along the vertical direction V and defines a groove for receiving the plate 242. Other suitable ways of mounting the plate 242 to the housing 102 are possible within the scope of the present invention.

[0064] This written description uses examples to disclose the invention, including the best mode, to enable any person skilled in the art to practice the invention, including making and using any devices or systems and performing any incorporated methods. The invention may include other examples that occur to those skilled in the art. If such other examples include structural elements that do not differ from the literal language of the invention, or if such other examples include equivalent structural elements with insubstantial differences from the literal language of the invention, such other examples are within the scope of the invention.

Claims

1. A linear compressor, defining an axial direction and a vertical direction, the linear compressor comprising: a housing defining an oil pan for collecting lubricant; a pump for circulating lubricant within the housing, the pump including a pump inlet located within the oil pan; and A heat dissipation assembly comprising: a plate mounted to an inner surface of the housing; and a fluid passage defined between the plate and the inner surface of the housing, the fluid passage having a fluid inlet for receiving the lubricant and a fluid outlet for discharging the lubricant back into the oil pan; the fluid inlet being located at the top of the plate along the vertical direction, and the fluid outlet being located at the bottom of the plate along the vertical direction.

2. The linear compressor according to claim 1, characterized in that The heat dissipation assembly further comprises: A supply pipe provides fluid communication between a hot oil collection point and the fluid inlet of the fluid passageway.

3. The linear compressor according to claim 1, wherein The fluid outlet is located at the bottom of the plate near the oil pan along the vertical direction.

4. The linear compressor according to claim 1, wherein The fluid outlet is disposed near the bottom of the oil pan.

5. The linear compressor according to claim 1, wherein The fluid passage is serpentine.

6. The linear compressor according to claim 1, wherein: The plate defines a plate groove that partially defines the fluid passageway.

7. The linear compressor according to claim 1, wherein The housing defines a housing recess that partially defines the fluid passageway.

8. The linear compressor according to claim 1, wherein The heat dissipation component includes: A plurality of plates are mounted to the inner surface of the housing to define a plurality of fluid passages.

9. The linear compressor according to claim 1, wherein: The plate is located at the lower portion of the housing.

10. The linear compressor according to claim 1, wherein The plate is curved to match the contour of the inner surface of the housing.

11. The linear compressor according to claim 1, wherein The plate defines a plate thickness and the housing defines a housing thickness, wherein the plate thickness is between 1 and 2 times the housing thickness.

12. The linear compressor according to claim 1, wherein The plate is formed of a heat insulating material.

13. The linear compressor according to claim 1, wherein The thermal conductivity of the plate is lower than that of the housing.

14. The linear compressor according to claim 1, wherein The panel is formed from a thermoplastic material.

15. The linear compressor according to claim 1, wherein The panel is formed from stamped sheet metal.

16. The linear compressor according to claim 1, wherein The heat dissipation assembly further comprises: A heat-insulating cover is located on the plate.

17. The linear compressor of claim 1, further comprising: A plurality of brackets are used to fix the plate on the shell.

18. The linear compressor according to claim 1, wherein The plate is mounted to the housing using one or more mechanical fasteners.

19. A heat sink assembly for a linear compressor, the linear compressor comprising a housing defining an oil pan for collecting lubricant, the heat sink assembly comprising: a plate mounted on the inner surface of the housing; and a fluid passage defined between the plate and the inner surface of the housing, the fluid passage having a fluid inlet for receiving lubricant and a fluid outlet for draining the lubricant back into the oil pan, the fluid inlet being located vertically at the top of the plate and the fluid outlet being located vertically at the bottom of the plate.

20. The heat dissipation assembly according to claim 19, wherein: The plate is formed of a heat insulating material having a lower thermal conductivity than that of the housing.

Images