Heat dissipation components for linear compressors

Abstract

A linear compressor (100) and a heat dissipation assembly (230) thereof. The linear compressor (100) includes a housing (102) defining a reservoir for collecting lubricant and a pump (206) for circulating the lubricant within the housing (102). The linear compressor (100) also includes a heat dissipation assembly (230) disposed within a cavity (108) and facilitating the discharge of heat energy from the cavity (108) to the exterior of the housing (102). The heat dissipation assembly (230) includes a distribution pipe (240) and a flow restriction member (270). The distribution pipe (240) is connected to a hot oil collection point (232) and defines a plurality of discharge ports for distributing lubricant (204) along the housing (102) and returning the lubricant (204) to the reservoir (202). The flow restriction member (240) can be disposed below the distribution pipe (240) or wrapped around the distribution pipe (240) to restrict the flow of the lubricant (204).

Description

Technical Field

[0001] The present invention generally relates to linear compressors, and more particularly 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. This sealed system typically includes a compressor, which generates compressed refrigerant during operation. The compressed refrigerant flows to an evaporator, where heat exchange between the refrigeration compartment and the refrigerant cools the refrigeration compartment and the food contained therein. 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 within a chamber. As the piston moves within the chamber, it compresses the refrigerant.

[0003] An oil supply or lubricant system is typically included within the compressor housing to lubricate the piston to reduce friction losses caused by the piston 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 is heated during operation of the compressor, the oil may become atomized or may otherwise splash around, which can lead to 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 transfer the hot oil to the outside of the housing, but these heat exchangers are complex, expensive, and prone to leaks.

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

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

[0006] In one exemplary embodiment, a compressor is provided, defining an axial and vertical orientation. The compressor includes a housing defining a reservoir for collecting lubricant; an inner housing disposed within the housing for slidably receiving a piston, the inner housing defining a hot oil collection point; and a pump for circulating lubricant within the housing, the pump including a pump inlet disposed within the reservoir. A heat dissipation assembly includes a distribution conduit extending along an inner surface of the housing, the distribution conduit defining a fluid inlet fluidly connected to the hot oil collection point for receiving lubricant, and a plurality of drain ports defined within the distribution conduit for allowing the lubricant to drip along the housing and return to the reservoir.

[0007] In another exemplary embodiment, a heat sink assembly for a compressor is provided. The compressor includes a housing defining a reservoir for collecting lubricant; an inner housing disposed within the housing for slidably receiving a piston, the inner housing defining a hot oil collection point; and a pump for circulating the lubricant within the housing. The heat sink assembly includes a distribution conduit extending along an inner surface of the housing, the distribution conduit defining a fluid inlet fluidly connected to the hot oil collection point for receiving the lubricant, and a plurality of drain ports defined within the distribution conduit for allowing the lubricant to drip along the housing and return to the reservoir.

[0008] These and other features, aspects and advantages of the present invention will become more readily understood with reference to the following description and appended claims.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] With reference to the accompanying drawings, the specification sets forth a complete disclosure of the present invention for those skilled in the art, which disclosure enables those skilled in the art to implement the present invention, including the best embodiment of the present invention.

[0010] Figure 1 is a front elevational 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 perspective cross-sectional view of a linear compressor according to an exemplary embodiment of the present invention.

[0013] Figure 4 According to an exemplary embodiment of the present invention Figure 3 Another perspective cross-sectional view of an exemplary linear compressor.

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

[0015] Figure 6 According to an exemplary embodiment of the present invention Figure 3 A cross-sectional view of an exemplary linear compressor with the piston in an extended position.

[0016] Figure 7 According to an exemplary embodiment of the present invention Figure 3 A cross-sectional view of an exemplary linear compressor with the piston in a retracted position.

[0017] Figure 8 A heat dissipation assembly according to an exemplary embodiment of the present invention is provided. Figure 3 Schematic cross-sectional view of an exemplary linear compressor.

[0018] Figure 9 Provided is a method according to an exemplary embodiment of the present invention including Figure 8 An exemplary heat sink assembly Figure 3 Top view of an exemplary linear compressor.

[0019] Figure 10 According to an exemplary embodiment of the present invention, Figure 8 Schematic diagram of certain components of an exemplary heat dissipation assembly.

[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] Reference will now be made in detail to embodiments of the present invention, one or more examples of which are shown in the accompanying drawings. Each example is provided in an illustrative manner and does not limit the present invention. In fact, it will be apparent to those skilled in the art that various modifications and variations can be made to the present invention without departing from the scope or spirit of the present invention. For example, a feature shown or described as part of one embodiment can be used in another embodiment, thereby producing yet another embodiment. Therefore, it is intended that the present invention covers these modifications and variations within the scope of the appended claims and their equivalents.

[0022] Figure 1 Depicted is a sealed refrigeration system 60 ( Figure 2 ) Refrigeration appliance 10. It should be understood that the term "refrigeration appliance" is used herein in a general 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 illustrated example embodiment, the refrigeration appliance 10 is depicted as an upright refrigerator having a cabinet or inner shell 12 defining a plurality of internal refrigerated storage compartments. Specifically, the 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. The upper drawer 20 and the lower drawer 22 are "pull-out" drawers that can be manually moved into and out of the lower freezer compartment 18 on a suitable sliding mechanism.

[0024] Figure 2 FIG2 is a schematic diagram of certain components of refrigeration appliance 10, including its sealed refrigeration system 60. A mechanical compartment 62 contains components for performing a known vapor compression cycle for cooling 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 appreciated 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] In the refrigeration system 60, the refrigerant flows into the compressor 64, which operates to increase the pressure of the refrigerant. Compressing the refrigerant increases its temperature, which is reduced by passing the refrigerant through the condenser 66. In the condenser 66, the refrigerant exchanges heat with the surrounding air to cool the refrigerant. C Illustratively, a fan 72 is used to drive air through the condenser 66 to provide forced convection for faster and more efficient heat exchange between the refrigerant within the condenser 66 and the surrounding air. Thus, as will be appreciated by those skilled in the art, increasing the airflow through the condenser 66 can improve the efficiency of the 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 restrictive device) receives refrigerant from the condenser 66. From the expansion device 68, the refrigerant enters the evaporator 70. Upon exiting the expansion device 68 and entering the evaporator 70, the refrigerant's pressure drops. Due to the refrigerant's pressure drop and phase change, the evaporator 70 becomes cooler relative to the upper fresh food compartment 14 and lower freezer compartment 18 of the refrigeration appliance 10. This produces cooled air and cools the upper fresh food compartment 14 and lower freezer compartment 18 of the refrigeration appliance 10. Thus, the evaporator 70 acts as a heat exchanger, transferring heat from the air passing through the evaporator 70 to the refrigerant flowing through the evaporator 70.

[0027] In general, the vapor compression cycle components, associated fans, and associated compartments in the refrigeration circuit are sometimes referred to as operable to force cool air through the lower freezer compartment 14, the lower freezer compartment 18 ( Figure 1 ) sealed refrigeration system. Figure 2 The refrigeration system 60 described in the foregoing is provided by way of example only. Thus, other configurations using refrigeration systems are also within the scope of the present invention.

[0028] Now the overall reference Figures 3 to 9 , a linear compressor 100 according to an exemplary embodiment of the present invention will be described. Specifically, Figure 3 and Figure 4 A perspective cross-sectional view of a linear compressor 100 is provided. Figure 5 A perspective view of a linear compressor 100 is provided with the compressor case or housing 102 removed for clarity, and Figure 6 and Figure 7 Cross-sectional views of a linear compressor are provided when the piston is in an extended position and a retracted position, respectively. It should be understood that linear compressor 100 is used herein only as an exemplary embodiment to facilitate the description of aspects of the present invention. Modifications and variations may be made to linear compressor 100 while remaining within the scope of the present invention.

[0029] For example Figure 3 and Figure 4 For example, the housing 102 can include a lower housing or lower shell 104 and an upper housing or upper shell 106, which are joined together to form a generally enclosed cavity 108 for accommodating the various components of the linear compressor 100. Specifically, for example, the cavity 108 can be an airtight or gastight shell that can accommodate the working components of the linear compressor 100 and can prevent or prevent refrigerant from leaking or escaping from the refrigeration system 60. In addition, the 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 is described and illustrated herein only to describe aspects of the present invention. Changes and modifications can be made to the linear compressor 100 while remaining within the scope of the present invention.

[0030] Now the overall reference Figures 3 to 9 , various parts and working components of the linear compressor 100 according to an exemplary embodiment will be described. As shown, the linear compressor 100 includes an inner shell 110, which extends, for example, along an axial direction A between a first end 112 and a second end 114. The inner shell 110 includes a cylinder 117 defining a chamber 118. The cylinder 117 is disposed at or adjacent to the first end 112 of the inner shell 110. The chamber 118 extends longitudinally along the axial direction A. As discussed in more detail below, the linear compressor 100 is operable to increase the pressure of the fluid 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 the linear compressor 100 can be used as a compressor 64 ( Figure 2 ) of refrigeration appliances 10 ( Figure 1 ).

[0031] The linear compressor 100 includes a stator 120 of a motor mounted or secured to the inner housing 110. For example, the stator 120 generally includes an outer back iron 122 extending around a circumference C within the inner housing 110 and a drive coil 124. The linear compressor 100 also includes one or more valves that allow refrigerant to enter and exit the chamber 118 during operation of the linear compressor 100. For example, a discharge muffler 126 is provided at one end of the chamber 118 for regulating the outflow of refrigerant from the chamber 118, while a suction valve 128 (for clarity, only shown) is provided at the end of the chamber 118. Figures 6 and 7 ) regulates the inflow of refrigerant to chamber 118.

[0032] A piston 130 having a piston head 132 is slidably received in the chamber 118 of the cylinder 117. Specifically, the piston 130 is slidable along the axial direction A. During the sliding movement of the piston head 132 in the chamber 118, the piston head 132 compresses the refrigerant in the chamber 118. As an example, the piston head 132 may be moved from a top dead center position (see, e.g., Figure 6 ) along the axial direction A towards the bottom dead center position (see e.g. Figure 7 ) slides, 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 in 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. Thus, in alternative exemplary embodiments, linear compressor 100 may include multiple piston heads.

[0033] As shown in the figure, the linear compressor 100 also includes a mover 140 for compressing refrigerant, which is generally driven by the stator 120. Specifically, for example, the mover 140 may include an inner back iron 142 disposed in the stator 120 of the motor. In particular, the outer back iron 122 and / or the drive coil 124 may extend around the inner back iron 142, for example, along the circumferential direction C. The inner back iron 142 also has an outer surface facing the outer back iron 122 and / or the drive coil 124. At least one drive magnet 144 is mounted to the inner back iron 142, for example, mounted on the outer surface of the inner back iron 142.

[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, for example, by an air gap in 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 approximately flush with the outer surface of the inner back iron 142. Thus, the drive magnet 144 can be inserted into the inner back iron 142. In this way, during operation of the linear compressor 100, the magnetic field from the drive coil 124 may only need to pass through a single air gap between the outer back iron 122 and the inner back iron 142, and the linear compressor 100 may be more efficient relative to a linear compressor having air gaps on both sides of the drive magnet.

[0035] As in Figure 3 As can be seen in FIG. 1 , the drive coil 124 extends, for example, along a circumferential direction C around the inner back iron 142. In an alternative exemplary embodiment, the inner back iron 142 may extend along the circumferential direction C around the drive coil 124. The drive coil 124 is operable to move the inner back iron 142 along the axial direction A during operation of the drive coil 124. For example, a current source (not shown) may induce a current within the drive coil 124 to generate a magnetic field that attracts the drive magnet 144 and forces the piston 130 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, during operation of the drive coil 124, the magnetic field of the drive coil 124 may attract the drive magnet 144 to move the inner back iron 142 and the piston head 132 along the axial direction A. Thus, 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, for example, by moving the inner back iron 142 along the axial direction A.

[0036] The linear compressor 100 may include various components for enabling 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 is in operable communication with the motor (e.g., the drive coil 124 of the motor), for example. Thus, the controller can selectively activate the drive coil 124, for example, by inducing a current in the drive coil 124, to compress the refrigerant using the piston 130 as described above.

[0037] The controller includes memory and one or more processing devices, such as a microprocessor, CPU, or the like, such as a general-purpose or special-purpose microprocessor. The microprocessor is operable to execute programmed instructions or microcontrol code related to the operation of the linear compressor 100. The memory can represent 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 on-board within the processor. Alternatively, the controller can be constructed without 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) to perform control functions, rather than 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 also has an inner surface disposed opposite the outer surface of the outer cylinder 146. The inner sleeve 148 is disposed 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 otherwise connected to the outer cylinder 146 via any other suitable mechanism or method.

[0039] The outer cylinder 146 can be constructed from or with any suitable material. For example, the outer cylinder 146 can be constructed from or with a plurality of (e.g., ferromagnetic) laminations. The laminations are arranged along a circumferential direction C to form the outer cylinder 146 and are mounted or secured to one another, for example, using rings pressed onto the ends of the laminations. The outer cylinder 146 can define a recess, for example, extending inward from an outer surface of the outer cylinder 146 along a radial direction R. The drive magnet 144 is disposed in the recess on the outer cylinder 146, for example, such that the drive magnet 144 is embedded within 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 an 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 so that movement of the inner back iron 142 along a radial direction R is prevented or restricted, while movement along the axial direction A is relatively unimpeded. Thus, the planar springs 150 can be substantially stiffer along the radial direction R than along the axial direction A. Thus, during operation of the motor and 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 pull forces from the motor from being transmitted to the piston 130 and causing friction losses in the cylinder 117.

[0041] The flexible mounting member 160 is mounted to the inner back iron 142 and extends through the inner back iron 142. Specifically, the flexible mounting member 160 is mounted to the inner back iron 142 via the inner sleeve 148. Thus, the flexible mounting member 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 mounting member 160 to mount or secure the flexible mounting member 160 to the inner sleeve 148. The flexible mounting member 160 can help form a coupling 162. The coupling 162 connects the inner back iron 142 and the piston 130 so that movement of the inner back iron 142, for example, along the axial direction A, is transmitted to the piston 130.

[0042] The coupling 162 may be a flexible coupling that is flexible or pliable along the radial direction R. In particular, the coupling 162 is relatively 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 to the piston 130 through the coupling 162. In this way, the side pull 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 can be reduced.

[0043] As can be seen in the figure, 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 on the cylinder 117 at the chamber 118, and the inner surface of the cylindrical sidewall 170 can be positioned opposite the outer surface of the cylindrical sidewall 170. Thus, 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.

[0044] The flexible mounting member 160 extends, for example, along the axial direction A between a first end 172 and a second end 174. According to an exemplary embodiment, the inner surface of the cylindrical sidewall 170 defines a ball seat 176 proximate the first end. In addition, the coupling 162 further includes a ball head 178. Specifically, for example, the ball head 178 is disposed at the first end 172 of the flexible mounting member 160, and the ball head 178 can contact the flexible mounting member 160 at the first end 172 of the flexible mounting member 160. In addition, the ball head 178 can contact the piston 130 at the ball seat 176 of the piston 130. In particular, the ball head 178 can rest on the ball seat 176 of the piston 130 so that the ball head 178 can slide and / or rotate on the ball seat 176 of the piston 130. For example, ball head 178 may have a truncated spherical surface that is positioned against ball seat 176 of piston 130, and ball seat 176 may be shaped to complement the truncated spherical surface of ball head 178. The truncated spherical surface of ball head 178 may slide and / or rotate on ball seat 176 of 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 inner 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 inner back iron 142 and the piston 130.

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

[0047] In addition, the flexible mount 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 mount 160 toward the piston head 132 and / or into the piston 130. The inner back iron 142 can be mounted, for example, to a mid-portion of the flexible mount 160 between the first end 172 and the second end 174 of the flexible mount 160, such that the inner back iron 142 extends around the tubular wall 190. The passage 192 can extend within the tubular wall 190 between the first end 172 and the second end 174 of the flexible mount 160, such that the compressible fluid can flow through the passage 192 from the first end 172 of the flexible mount 160 to the second end 174 of the flexible mount 160. In this manner, during operation of the linear compressor 100, the compressible fluid can flow through the inner back iron 142 within the flexible mount 160. A muffler 194 may be disposed within the passage 192 within the tubular wall 190 , for example, 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 pass through the piston head 132 via the opening 196 of the piston head and into the chamber 118. In this way, the fluid (compressed by the piston head 132 in the chamber 118) can flow through the flexible mount 160 and the inner back iron 142 in the passage 192 to the piston 130. As described above, the suction valve 128 ( Figures 6 and 7 ) may be provided on the piston head 132 to regulate the flow of compressible fluid through the opening 196 into the chamber 118 .

[0049] Still refer to Figures 3 to 9 , 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 can be applied to any other suitable compressor or machine requiring continuous lubrication.

[0050] As shown, the housing 102 generally defines a reservoir 202 configured to collect lubricant (e.g., as shown herein by reference numeral 204, see Figure 8 ). Specifically, a reservoir 202 is defined in the bottom of the lower housing 104. The lubrication system 200 also includes a pump 206 for continuously circulating the lubricant 204 through the components of the linear compressor 100 that require lubrication. In this regard, for example, the pump 206 may include a pump inlet 208 that is disposed proximate to the bottom of the housing 102 within the reservoir 202. For example, via a supply line 210 ( Figure 7 ) before circulating the oil 206 through the linear compressor 100, the pump 206 can draw lubricant 204 from the sump 202 through the pump inlet 208. Although only one supply conduit 210 is shown for clarity, it should be understood that the lubrication system 200 can include any suitable number of supply conduits, nozzles, and other distribution features to provide lubricant 204 to the various components of the linear compressor 100.

[0051] Obviously, according to the illustrated embodiment, the pump inlet 208 is disposed very close to and facing the bottom of the lower housing 104. Thus, the pump 206 can easily draw in the lubricant 204 even when the oil level is low. Specifically, the linear compressor 100 can be configured to receive lubricant 204 that does not exceed the maximum fill line 212. For example, the maximum fill line 212 may be as shown in FIG. Figure 8, and for example, the maximum fill line can be less than halfway up the lower housing 1, or less than a quarter of the way up, or lower. During operation, the pump 206 can circulate the lubricant 204 throughout the linear compressor 100 before recirculation, as will be described in further detail below. Although not illustrated herein, it should be understood that the lubrication system 200 can include various features for treating, filtering, or conditioning the lubricant 204 during recirculation, such as various filters, screens, etc. Additionally, it should be understood that although the pump 206 is illustrated as being disposed within the reservoir 202, it can be disposed at any other location and can include a fluid passage for extracting the lubricant 204 from the reservoir 202.

[0052] As also shown in the example, the linear compressor 100 can include a suction port 220 for receiving a flow of refrigerant. Specifically, the suction port 220 can be defined on the housing 102 (e.g., such as on the lower housing 104) and can be configured to receive a refrigerant supply line to provide refrigerant to the chamber 108. As described above, the flexible mount 160 includes a tubular wall 190 that defines a passage 192 for directing a compressible fluid, such as refrigerant gas, through the flexible mount 160 toward the piston head 132. Thus, the desired flow path of 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 can block the opening 196 during the compression stroke, and the discharge valve 116 can allow the compressed gas to exit the chamber 118 when a desired pressure is reached.

[0053] The flexible mounting member 160 may also define a channel inlet 222, which is arranged near the second end 174 of the flexible mounting member 160 for drawing gas from the suction port 220 or the cavity 108 into the channel 192. Specifically, the channel inlet 222 can be an opening on the flexible mounting member 160, which extends roughly in a horizontal plane (the same vertical plane) and opens toward the suction port 220. Specifically, according to the illustrated embodiment, the channel inlet 222 and the suction port 220 can be roughly arranged in the same horizontal plane. According to the illustrated embodiment, the suction port 220 and the channel inlet 222 are also arranged along the vertical V to be close to the midpoint of the housing 102. However, it should be understood that, according to optional embodiments, the suction port 220 and the channel inlet 222 can be arranged at any other suitable position in the housing 102.

[0054] Now refer to Figures 6 to 10, the linear compressor 100 may also include features for exhausting or dissipating heat that has accumulated in the oil or lubricant within the linear compressor 100 or elsewhere. Specifically, according to an exemplary embodiment, the linear compressor 100 includes a heat sink assembly 230 that is disposed within the cavity 108 and helps promote the discharge of thermal energy from within the cavity 108 to the exterior of the housing 102. Although an exemplary heat sink assembly 230 is described herein, it should be understood that various changes and modifications can be made to the heat sink assembly 230 while remaining within the scope of the present invention. For purposes of explaining aspects of the present invention, the heat sink assembly 230 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 230 can be used in other compressors and other lubrication systems while remaining within the scope of the present invention.

[0055] Generally, the heat sink assembly 230 discharges or drains the heat absorbed by 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 parts of the linear compressor 100 to the hot oil collection point 232. In this regard, the heat sink assembly 230 can have any suitable mechanism, conduit, or other features for collecting the lubricant 204 and draining it through the hot oil collection point 232 so that it can be cooled by the heat sink assembly 230, returned to the sump 202, and recirculated. For example, according to one exemplary embodiment, the hot oil collection point 232 can be defined on the inner housing 110 for passing the heated lubricant 204 through the inner housing 110.

[0056] like Figures 6 to 10As best shown in FIG, the heat sink assembly 230 includes a distribution conduit 240 extending along an inner surface 242 of the housing 102. The distribution conduit 240 defines a fluid inlet 244 fluidly coupled to a hot oil collection point 232 on the inner housing 110. The distribution conduit may also define a plurality of discharge ports 246 configured to spray, drip, or otherwise deposit lubricant 204 along the housing 102 so that the lubricant flow can be recollected in the sump 202 before being recirculated by the pump 206. In this way, the lubricant 204 is pushed through the working components of the linear compressor 100 to minimize friction and improve operating efficiency, with the oil absorbing heat during the process. The heated lubricant 204 then exits the inner housing 110 through the hot oil collection point 232, where it is distributed within the distribution conduit 240 around the housing 102. The heated oil 204 is then sprayed onto the housing 102 at a lower temperature than the heated lubricant 204. As the heated lubricant 204 flows down the housing 102 and is recollected in the sump 202, heat energy can be transferred from the lubricant 204 to the housing 102, where it can be discharged to the surrounding environment. In this way, the lubricant 204 can be recirculated at a cooler temperature, thereby improving the performance and life of the linear compressor 100.

[0057] In general, the distribution conduit 240 can be fluidly coupled to any point on the inner shell 110 in any manner or by any mechanism for receiving the heated lubricant 204. For example, according to the illustrated embodiment, the heat dissipation assembly 230 includes a supply conduit 250 that extends between the hot oil collection point 232 and the fluid inlet 244 of the distribution conduit 240 and provides fluid communication therebetween. In this regard, for example, the supply conduit 250 can be a flexible conduit extending from the hot oil collection point 232 to the distribution conduit 240. According to alternative embodiments, the distribution conduit 240 can be coupled directly to the inner shell, for example, via the hot oil collection point 232 or through any other outlet of the inner shell 110.

[0058] The distribution duct 240 can generally have any suitable size, location, and configuration for distributing the lubricant 204 as needed to facilitate operation of the heat sink assembly 230 and cooling of the linear compressor 100. For example, according to the illustrated embodiment, the distribution duct 240 extends around the entire circumference of the housing 102 within a single horizontal plane. More specifically, according to the illustrated embodiment, the distribution duct 240 is a circular duct that is directly mounted to the lower housing 104 via a mounting bracket 252. Generally, the mounting bracket 252 is configured to reduce the transmission of vibrations from the distribution duct 240 to the housing 102.

[0059] While the distribution duct 240 is illustrated as being mounted directly to the lower housing 104, it should be understood that any other suitable mounting locations and mechanisms may be used according to alternative embodiments. For example, according to alternative embodiments, the distribution duct 240 may be mounted directly to the inner shell 110, allowing the distribution duct 240 to simply hang adjacent to the housing 102. Alternatively, the distribution duct 240 may be mounted within the upper housing 106, allowing the heated lubricant 204 to drain over a larger surface area of ​​the housing 102 before being collected within the sump 202. Furthermore, while the distribution duct 240 is illustrated as a circular duct extending in a single horizontal plane, it should be understood that the distribution duct may have any other suitable cross-sectional shape and may extend through the housing in any other suitable pattern or position (e.g., in a serpentine manner, a zigzag pattern, etc.). Other configurations are possible and within the scope of the present invention.

[0060] According to exemplary embodiments, distribution conduit 240 can be formed from any material that is sufficiently rigid to maintain a fluid channel and accommodate the flow of lubricant 204 therein. For example, according to the illustrated embodiment, distribution conduit 240 is a small tube formed from metal. According to alternative embodiments, distribution conduit 240 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), perfluoroalkoxy (PFA), fluorinated ethylene propylene (FEP), or acrylonitrile butadiene styrene (ABS). Alternatively, according to exemplary embodiments, these components can be extruded (tubing), compression molded, for example, using sheet molding compound (SMC) thermoset plastic or other thermoplastics. According to other embodiments, distribution conduit 240 can be formed from any other suitable rigid material.

[0061] The discharge ports 246 defined as the distribution conduit 240 can have any suitable number, shape, size, and configuration to appropriately direct the flow of heated lubricant 204 to a desired portion of the housing 102. For example, according to the illustrated embodiment, the plurality of discharge ports 246 includes greater than 10, greater than 25, greater than 50, greater than 75, or greater than 100 discharge ports 246 equally spaced along the length of the distribution conduit 240. According to still other embodiments, the distribution conduit 240 can define regions that do not include discharge ports 246, such as at certain locations where distribution of the lubricant 204 may be undesirable, such as, for example, near the suction port 220.

[0062] According to an exemplary embodiment, the discharge ports 246 are simple orifices 260 drilled, machined, stamped, or otherwise formed within the distribution conduit 240. According to other embodiments, each discharge port 246 may include a discharge nozzle mounted above the orifice 260 for selectively controlling the flow rate and direction of the lubricant 204. According to the illustrated embodiment, the discharge ports 246 (e.g., orifices 260) are defined on the bottom side 262 of the distribution conduit 240. However, according to alternative embodiments, the discharge ports 246 may be defined on the side, top, or any other suitable location along the distribution conduit 240. For example, the discharge ports 246 may be angled vertically downward and away from the vertical centerline of the linear compressor 100. In this manner, the lubricant 204 is forced directly toward the lower housing 104 and downward into the sump 202. According to other embodiments, the discharge ports 246 may be arranged and oriented in any other suitable manner to direct the lubricant 204 onto the inner surface 242 of the housing 102.

[0063] It is worth noting that due to the pressure and flow of the lubricant 204 within the distribution conduit 240, it may be desirable to restrict the flow, for example, to prevent splashing and / or atomization of the lubricant 204. Figure 10 As best shown in FIG, the heat sink assembly 230 further includes one or more flow restriction members 270 disposed above the drain port 246 for restricting the lubricant 204 from passing through the drain port 246. For example, Figure 10 260 . It will be appreciated that these flow restricting members 270 may be used individually or in combination with one another. Specifically, the flow restricting member 270 may include a coiled spring element 272 that extends around the outer diameter of the distribution conduit 240 and is used to restrict flow out of the outlet ports 246. According to alternative embodiments, the flow restricting member 270 may be a braid or screen 274 disposed over the plurality of outlet ports 246 for restricting flow therethrough. It will be appreciated that any suitable flow restricting member 270 may be used according to alternative embodiments. For example, a cross member or screen may be formed within the orifice 260 during the manufacturing process, or the cross member or screen may be overmolded onto the distribution conduit 240 after the distribution conduit is constructed.

[0064] The heat sink assembly 230 described above can be used to cool the operation of a linear compressor (such as linear compressor 100 or any other compressor). Specifically, the heat sink assembly 230 may utilize a mechanism for spraying oil onto the walls of the compressor housing to achieve improved heat removal and compressor efficiency. Specifically, according to an exemplary embodiment, the heat sink assembly 230 utilizes a spraying mechanism (e.g., distribution conduit 240) to uniformly and controllably spray oil onto the inner surface of the housing, transferring heat to the outer wall. The slow flow of oil within the wall allows the oil to cool.

[0065] Distribution conduit 240 operates by receiving hot oil exiting the cylinder under the force of pump 206. Distribution conduit 240 is provided with multiple holes (e.g., discharge port 246), through which oil is forced out along the outer periphery of the bottom portion. The oil flows downward along the wall, surrounding the entire lower housing inner wall portion (losing heat to the wall). The slow-flowing oil drips along the wall, allowing the oil to cool before reaching the sump. The oil remains in liquid form and releases minimal heat to the intake air inside the housing. As the oil flows out of the holes in the conduit, the flow can be slowed by using porous or flow-restricting surfaces (e.g., flow-restricting member 270). For example, a tight-fitting spring can be used to cover the outer diameter of distribution conduit 240 and provide further flow resistance without atomizing the oil. Alternatively, a similar material, such as a screen or braided nylon or other polymer material, can be used to introduce oil flow resistance. This flow-restricting material allows the oil to flow evenly down the inner wall (also providing a built-in debris filter as the oil flows through the sock or spring structure placed on distribution conduit 240). By starting with the hottest oil at the top of the structure, the oil flows down to the bottom, where it cools in a sump before being recirculated to the oil pump and compression cylinders and pistons, where the oil regains heat in a continuous cycle, the present invention provides a low-cost method of achieving better efficiency and avoids additional brazing joints on the outside of the shell.

[0066] This written description uses examples to disclose the invention, including the best mode, and also to enable any person skilled in the art to practice the invention, including making and using any devices or systems and performing any included methods. The patentable scope of the invention is defined by the claims and 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 claims, or if such other examples include equivalent structural elements with insubstantial differences from the literal language of the claims, such other examples are intended to be within the scope of the claims.

Claims

1. A compressor with limited axial and vertical directions, characterized in that The compressor comprises: a housing defining a sump for collecting lubricant; an inner shell disposed within the housing for slidably receiving the piston, the inner shell defining a hot oil collection point; a pump for circulating the lubricant within the housing, the pump including a pump inlet disposed within the reservoir; and A heat dissipation component, comprising: a distribution conduit extending along an inner surface of the housing, the distribution conduit defining a fluid inlet fluidly connected to the hot oil collection point for receiving the lubricant; and a plurality of drain ports disposed within the distribution conduit for allowing the lubricant to drip down the housing and back into the reservoir; The heat dissipation component further includes: A flow restriction member is disposed above the plurality of discharge ports and is configured to restrict the lubricant from passing through the plurality of discharge ports.

2. The compressor according to claim 1, characterized in that The plurality of discharge openings are equally spaced along the length of the distribution conduit.

3. The compressor according to claim 1, characterized in that The plurality of outlet ports includes greater than 50 orifices.

4. The compressor according to claim 1, characterized in that Each of the plurality of drain ports is configured and oriented to direct the lubricant onto the inner surface of the housing.

5. The compressor according to claim 1, characterized in that Each of the plurality of discharge ports is defined on a bottom portion of the distribution conduit.

6. The compressor according to claim 1, characterized in that Each of the plurality of discharge openings is an orifice or a discharge nozzle.

7. The compressor according to claim 1, characterized in that The flow restriction member is a resilient element extending around the dispensing conduit.

8. The compressor according to claim 1, characterized in that The flow restriction member is a braid or a mesh disposed over the plurality of outlet ports.

9. The compressor according to claim 1, characterized in that The distribution conduit extends around the entire circumference of the housing.

10. The compressor according to claim 1, characterized in that The compressor is a linear compressor.

11. The compressor according to claim 1, characterized in that The heat dissipation component further includes: A supply pipe provides fluid communication between the hot oil collection point and the fluid inlet of the distribution conduit.

12. The compressor according to claim 1, characterized in that The distribution conduit is directly attached to the housing.

13. A heat dissipation assembly for a compressor, characterized in that: The compressor includes: a housing defining a reservoir for collecting lubricant; an inner housing disposed within the housing for slidably receiving a piston, the inner housing defining a hot oil collection point; and a pump for circulating the lubricant within the housing, the heat dissipation assembly including: a distribution conduit extending along an inner surface of the housing, the distribution conduit defining a fluid inlet fluidly connected to the hot oil collection point for receiving the lubricant; and a plurality of drain ports defined in the distribution conduit for allowing the lubricant to drip down the housing and back into the reservoir; Also includes: A flow restriction member is disposed above the plurality of discharge ports and is configured to restrict the lubricant from passing through the plurality of discharge ports.

14. The heat dissipation assembly according to claim 13, wherein: The plurality of outlet ports includes more than 50 ports equally spaced along the length of the distribution conduit.

15. The heat dissipation assembly according to claim 13, wherein: Each of the plurality of discharge ports is defined on a bottom portion of the distribution conduit.

16. The heat dissipation assembly according to claim 13, wherein: The flow restriction member is a resilient element extending around the distribution conduit or a braid or mesh disposed over the plurality of outlet ports.

17. The heat dissipation assembly according to claim 13, wherein: The distribution conduit extends around the entire circumference of the lower portion of the housing, and a supply pipe provides fluid communication between the hot oil collection point and the fluid inlet of the distribution conduit.

18. The heat dissipation assembly according to claim 13, wherein: The compressor is a linear compressor.

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