CN116324163A

CN116324163A - Heat radiation assembly of linear compressor

Info

Publication number: CN116324163A
Application number: CN202180068479.0A
Authority: CN
Inventors: 格雷戈里·威廉·哈恩; 安德烈·P·维尼克
Original assignee: Qingdao Haier Refrigerator Co Ltd; Haier Smart Home Co Ltd; Haier US Appliance Solutions Inc
Current assignee: Qingdao Haier Refrigerator Co Ltd; Haier Smart Home Co Ltd; Haier US Appliance Solutions Inc
Priority date: 2020-10-07
Filing date: 2021-09-27
Publication date: 2023-06-23
Also published as: KR20230058719A; WO2022073436A1; EP4206466A1; EP4206466A4; US20220106953A1

Abstract

A linear compressor (100) and a heat dissipating assembly (230) thereof. The linear compressor (100) includes a housing (102) defining a sump for collecting lubricant and a pump (206) for circulating the lubricant within the housing (102). Also included is a heat dissipating assembly (230), the heat dissipating assembly (230) disposed within the cavity (108) and facilitating the discharge of thermal energy from within the cavity (108) to an exterior of the housing (102). The heat sink assembly (230) includes a distribution conduit (240) and a flow restricting member (270), the distribution conduit (240) being connected to the hot oil collection point (232) and defining a plurality of discharge ports for distributing lubricant (204) along the housing (102) and returning the lubricant (204) to the sump (202). The flow restricting member (240) may be disposed below the distribution pipe (240) or wrapped around the distribution pipe (240) to restrict the flow of lubricant (204).

Description

Heat radiation assembly of linear compressor

Technical Field

The present invention relates generally to linear compressors and, more particularly, to a heat dissipation system for a linear compressor.

Background

Some refrigeration appliances include a sealing system for cooling the refrigeration compartment of the refrigeration appliance. Sealing systems typically include a compressor that generates compressed refrigerant during operation of the sealing system. The compressed refrigerant flows to an evaporator where heat exchange between the refrigeration compartment and the refrigerant cools the refrigeration compartment and food items located therein. Recently, some refrigeration appliances include a linear compressor for compressing a refrigerant. Linear compressors typically include a piston and a drive coil. The drive coil generates a force for sliding the piston forward within the chamber. During movement of the piston within the chamber, the piston compresses the refrigerant.

An oil supply or lubricant system is typically included within the compressor housing for lubricating the pistons to reduce friction losses due to friction of the pistons against the chamber walls, which can negatively impact the efficiency of the associated refrigeration appliance. However, such linear compressors often experience performance problems when the oil temperature is high. For example, when oil is heated during operation of the compressor, the oil may be atomized or may otherwise splash around, which may result in mechanical losses in the spring or reliability problems related to entrainment of oil droplets into the suction gas port. Some linear compressors include external heat exchangers that transfer hot oil to the outside of the casing, but these heat exchangers are complex, expensive, and prone to leakage.

Therefore, a linear compressor having features for improved performance would be desirable. More particularly, a linear compressor with an improved system for dissipating heat from oil would be particularly beneficial.

Disclosure of Invention

Various aspects and advantages of the 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 invention.

In one exemplary embodiment, a compressor is provided that defines an axial direction and a vertical direction. The compressor includes: a housing defining a sump for collecting lubricant; an inner housing disposed within the housing for slidably receiving the piston, the inner housing defining a hot oil collection point; a pump for circulating lubricant within the housing, the pump including a pump inlet disposed within the sump. The heat dissipating 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 dripping the lubricant along the housing and back into the sump.

In another exemplary embodiment, a heat dissipating assembly for a compressor is provided. The compressor includes: a housing defining a sump for collecting lubricant; an inner housing disposed within the housing for slidably receiving the piston, the inner housing defining a hot oil collection point; and a pump for circulating the lubricant within the housing. The heat dissipating 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 dripping the lubricant along the housing and back into the sump.

These and other features, aspects, and advantages of the present invention will become better understood with regard 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 invention and together with the description, serve to explain the principles of the invention.

Drawings

A full disclosure of the present invention, including the best mode thereof, directed to one of ordinary skill in the art, is set forth in the specification, which makes reference to the appended drawings.

Fig. 1 is a front elevation view of a refrigeration appliance according to an exemplary embodiment of the present invention.

Fig. 2 is a schematic diagram of certain components of the exemplary refrigeration appliance of fig. 1.

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

Fig. 4 is another perspective cross-sectional view of the exemplary linear compressor of fig. 3 according to an exemplary embodiment of the present invention.

Fig. 5 is a perspective view of a linear compressor according to an exemplary embodiment of the present invention, with a compressor housing removed for clarity.

Fig. 6 is a cross-sectional view of the exemplary linear compressor of fig. 3 with the piston in an extended position in accordance with an exemplary embodiment of the present invention.

Fig. 7 is a cross-sectional view of the exemplary linear compressor of fig. 3 with the piston in a retracted position in accordance with an exemplary embodiment of the present invention.

Fig. 8 provides a schematic cross-sectional view of the exemplary linear compressor of fig. 3 including a heat dissipating assembly according to an exemplary embodiment of the present invention.

FIG. 9 provides a top view of the example linear compressor of FIG. 3 including the example heat dissipating assembly of FIG. 8 in accordance with an example embodiment of the present invention.

Fig. 10 provides a schematic diagram of certain components of the example heat dissipating assembly of fig. 8, in accordance with an example embodiment of the present invention.

Repeated use of reference characters in the specification and drawings is intended to represent the same or analogous features or elements of the invention.

Detailed Description

Reference now will be made in detail to embodiments of the invention, one or more examples of which are illustrated in the drawings. Each example is given by way of explanation of the invention, and is not to be construed as limiting the invention. Indeed, 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 invention. For instance, features illustrated or described as part of one embodiment can be used with another embodiment to yield a still further embodiment. Accordingly, it is intended that the present invention cover the modifications and variations of this invention provided they come within the scope of the appended claims and their equivalents.

Fig. 1 depicts a refrigeration appliance 10 including a sealed refrigeration system 60 (fig. 2). It should be understood that the term "refrigeration appliance" is used herein in a generic sense to encompass any manner of refrigeration appliance, such as an ice bin, a refrigerator/ice bin combination, and any make or model of conventional refrigerator. In addition, 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 in an air conditioning unit or air compression in an air compressor.

In the illustrated example embodiment shown in fig. 1, the refrigeration appliance 10 is depicted as an upright refrigerator having a cabinet or inner housing 12 defining a plurality of internally cooled storage compartments. In particular, 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 lower drawer 22 are "pull-out" drawers that can be manually moved into and out of the freezer compartment 18 on a suitable sliding mechanism.

Fig. 2 is a schematic diagram of certain components of the refrigeration appliance 10, including a sealed refrigeration system 60 of the refrigeration appliance 10. The machine chamber 62 contains components for performing a known vapor compression cycle of cooling air. These components include a compressor 64, a condenser 66, an expansion device 68, and an evaporator 70 connected in series and filled with refrigerant. As will be appreciated by those skilled in the art, the refrigeration system 60 may include additional components, such as at least one additional evaporator, compressor, expansion device, and/or condenser. As an example, the refrigeration system 60 may include two evaporators.

Within the refrigeration system 60, the refrigerant flows into a compressor 64 that operates to increase the pressure of the refrigerant. The compressed refrigerant increases its temperature, which is reduced by flowing the refrigerant through the condenser 66. Within the condenser 66, the refrigerant exchanges heat with ambient air to cool the refrigerant. As indicated by arrow A _C Illustratively, a fan 72 is used to drive air through the condenser 66 to provide forced convection for faster and efficient heat exchange between the refrigerant within the condenser 66 and the surrounding air. Thus, as known to those skilled in the art, increasing the airflow through the condenser 66 may increase the efficiency of the condenser 66, for example, by improving the cooling of the refrigerant contained therein.

An expansion device 68 (e.g., a valve, capillary tube, or other restriction device) receives refrigerant from the condenser 66. From the expansion device 68, the refrigerant enters an evaporator 70. Upon exiting the expansion device 68 and entering the evaporator 70, the pressure of the refrigerant drops. The evaporator 70 is cool relative to the

chambers

14 and 18 of the refrigeration appliance 10 due to the pressure drop and phase change of the refrigerant. Whereby cooling air can be generated and the

compartments

14 and 18 of the refrigeration appliance 10 can be refrigerated. Thus, the evaporator 70 is a heat exchanger that transfers heat from the air passing through the evaporator 70 to the refrigerant flowing through the evaporator 70.

In general, the vapor compression cycle components, associated fans, and associated compartments in the refrigeration circuit are sometimes referred to as a sealed refrigeration system operable to force cool air through the compartments 14, 18 (fig. 1). The refrigeration system 60 depicted in fig. 2 is provided by way of example only. Thus, other configurations using a refrigeration system are within the scope of the invention.

Referring now generally to fig. 3 to 9, a linear compressor 100 according to an exemplary embodiment of the present invention will be described. In particular, fig. 3 and 4 provide perspective cross-sectional views of the linear compressor 100, fig. 5 provides a perspective view of the linear compressor 100 with the compressor housing or shell 102 removed for clarity, and fig. 6 and 7 provide cross-sectional views of the linear compressor with the piston in an extended position and a retracted position, respectively. It should be understood that the linear compressor 100 is used herein as an exemplary embodiment only to facilitate the description of aspects of the present invention. Modifications and variations of the linear compressor 100 may be made while remaining within the scope of the present invention.

For example, fig. 3 and 4 illustrate that the housing 102 may include a lower or lower housing 104 and an upper or upper housing 106 that are joined together to form a generally enclosed cavity 108 for housing the various components of the linear compressor 100. Specifically, for example, the cavity 108 may be an airtight or airtight shell that may house the working components of the linear compressor 100 and may prevent or inhibit leakage or escape of refrigerant 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. Variations and modifications may be made to the linear compressor 100 while remaining within the scope of the present invention.

Referring now generally to fig. 3-9, 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 extending between a first end 112 and a second end 114, for example, along an axial direction a. The inner housing 110 includes a cylinder 117 defining a chamber 118. The air cylinder 117 is disposed at or adjacent the first end 112 of the inner housing 110. The chamber 118 extends longitudinally along the axis 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 may be used to compress any suitable fluid, such as refrigerant or air. In particular, the linear compressor 100 may be used in a refrigeration appliance, such as the refrigeration appliance 10 (fig. 1) in which the linear compressor 100 may be used as the compressor 64 (fig. 2).

The linear compressor 100 includes a stator 120 of a motor mounted or fixed to the inner casing 110. For example, the stator 120 generally includes an outer back iron 122 and a drive coil 124 extending within the inner casing 110 about the circumferential direction C. The linear compressor 100 also includes one or more valves that allow refrigerant to enter and leave 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 (shown only in fig. 6-7 for clarity) regulates the inflow of refrigerant to the chamber 118.

A piston 130 having a piston head 132 is slidably received within the chamber 118 of the cylinder 117. In particular, the piston 130 is slidable along the axial direction a. During sliding movement of the piston head 132 within the chamber 118, the piston head 132 compresses the refrigerant within the chamber 118. As an example, piston head 132 may slide within chamber 118 from a top dead center position (see, e.g., fig. 6) toward a bottom dead center position (see, e.g., fig. 7) along axial direction a, i.e., an expansion stroke of piston head 132. When the piston head 132 reaches the bottom dead center position, the piston head 132 changes direction and slides back toward the top dead center position in the chamber 118, i.e., the compression stroke of the piston head 132. It should be appreciated that the linear compressor 100 may include additional piston heads and/or additional chambers at opposite ends of the linear compressor 100. Thus, in alternative exemplary embodiments, the linear compressor 100 may have multiple piston heads.

As illustrated, the linear compressor 100 further includes a mover 140 for compressing a refrigerant, which is generally driven by the stator 120. Specifically, for example, the mover 140 may include an inner back iron 142 provided 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 at an outer surface of the inner back iron 142.

The drive magnet 144 may face and/or be exposed to the drive coil 124. In particular, the drive magnet 144 may be spaced apart from the drive coil 124, for example, by an air gap in the radial direction R. Thus, an air gap may be defined between the opposing surfaces of the drive magnet 144 and the drive coil 124. The drive magnet 144 may also be mounted or secured to the inner back iron 142 such that the outer surface of the drive magnet 144 is substantially flush with the outer surface of the inner back iron 142. Thereby, the driving magnet 144 may be inserted into the inner back iron 142. As such, during operation of the linear compressor 100, the magnetic field from the drive coil 124 may only need to traverse 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.

As can be seen in fig. 3, the drive coil 124 extends around the inner back iron 142, for example, along the circumferential direction C. In alternative example embodiments, the inner back iron 142 may extend around the drive coil 124 along the circumferential direction C. 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. As an example, a current source (not shown) may induce a current in the drive coil 124 to generate a magnetic field that attracts the drive magnet 144 and pushes the piston 130 to move along the axial direction a to compress the refrigerant within the chamber 118 as described above and as will be appreciated 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 slide the piston 130 between the top dead center position and the bottom dead center position, for example, by moving the inner back iron 142 along the axial direction a.

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

The controller includes a memory and one or more processing devices, such as a microprocessor, CPU, or the like, such as a general purpose or special purpose microprocessor, operable to execute programmed instructions or micro-control code associated with the operation of the linear compressor 100. The memory may represent a random access memory such as DRAM or a read only memory such as ROM or FLASH. The processor executes programming instructions stored in the memory. The memory may be a separate component from the processor or may be included on a board within the processor. Alternatively, the controller may be configured to perform control functions without the use of a microprocessor, for example, using a combination of discrete analog and/or digital logic circuits (such as switches, amplifiers, integrators, comparators, flip-flops, and gates, etc.), rather than relying on software.

The inner back iron 142 also includes an outer cylinder 146 and an inner sleeve 148. The outer cylinder 146 defines an outer surface of the inner back iron 142 and also has an inner surface disposed opposite the outer surface of the outer cylinder 146. An 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 may couple or secure the outer cylinder 146 and the inner sleeve 148 together. In alternative exemplary embodiments, inner sleeve 148 may be welded, glued, fastened, or otherwise connected to outer cylinder 146 via any other suitable mechanism or method.

Outer cylinder 146 may be constructed of or from any suitable material. For example, outer cylinder 146 may be constructed from or with a plurality of (e.g., ferromagnetic) laminations. The laminations are distributed along the circumferential direction C so as to form an outer cylinder 146 and are mounted to each other or fixed together, for example with a ring pressed onto the ends of the laminations. Outer cylinder 146 may define a recess extending inwardly from an outer surface of outer cylinder 146, for example, along radial direction R. The drive magnet 144 is disposed in a recess on the outer cylinder 146, for example, such that the drive magnet 144 is embedded within the outer cylinder 146.

The linear compressor 100 further includes a pair of planar springs 150. Each planar spring 150 may 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 spring 150 supports the inner back iron 142. In particular, the inner back iron 142 is suspended within the stator or motor of the linear compressor 100 by a planar spring 150 such that movement of the inner back iron 142 in the radial direction R is prevented or limited while movement in the axial direction a is relatively unimpeded. Thus, the planar spring 150 may be substantially stiffer along the radial direction R than along the axial direction a. In this way, the planar spring 150 may help maintain the uniformity of the air gap between the drive magnet 144 and the drive coil 124, for example, along the radial direction R during operation of the motor and movement of the inner back iron 142 in the axial direction a. The flat spring 150 may also help to prevent the side pull of the motor from being transferred to the piston 130 and causing frictional losses in the cylinder 117.

The flexible mount 160 is mounted to the inner back iron 142 and extends through the inner back iron 142. In particular, the flexible mount 160 is mounted to the inner back iron 142 via the inner sleeve 148. Thus, the flexible mount 160 may be coupled (e.g., threaded) to the inner sleeve 148 at the inner sleeve 148 and/or an intermediate portion of the flexible mount 160 to mount or secure the flexible mount 160 to the inner sleeve 148. The flexible mount 160 may help form a coupling 162. The coupling 162 connects the inner back iron 142 and the piston 130 such that movement of the inner back iron 142 is transferred to the piston 130, for example, along the axial direction a.

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 in the radial direction R such that little or no movement of the inner back iron 142 in the radial direction R is transferred through the coupling 162 to the piston 130. In this way, the side pull 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.

As can be seen in the figures, the piston head 132 of the piston 130 has a piston cylindrical side wall 170. The cylindrical sidewall 170 may 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 may slide over the cylinder 117 at the chamber 118 and the inner surface of the cylindrical sidewall 170 may be positioned opposite the outer surface of the cylindrical sidewall 170. Thus, the outer surface of the cylindrical sidewall 170 may face away from the center of the cylindrical sidewall 170 along the radial direction R, and the inner surface of the cylindrical sidewall 170 may face toward the center of the cylindrical sidewall 170 along the radial direction.

The flexible mount 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 the cylindrical sidewall 170 defines a ball seat 176 proximate the first end. In addition, the coupling 162 also includes a ball head 178. Specifically, for example, the ball head 178 is disposed at the first end 172 of the flexible mount 160, and the ball head 178 may contact the flexible mount 160 at the first end 172 of the flexible mount 160. Additionally, ball head 178 may contact piston 130 at ball seat 176 of piston 130. In particular, ball head 178 may rest on ball seat 176 of piston 130 such that ball head 178 may slide and/or rotate on ball seat 176 of piston 130. For example, the ball head 178 may have a frusto-spherical surface that is positioned against the ball seat 176 of the piston 130, and the ball seat 176 may be shaped to complement the frusto-spherical surface of the ball head 178. The frusto-spherical surface of ball head 178 may slide and/or rotate on ball seat 176 of piston 130.

For example, relative movement 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 may reduce friction between the piston 130 and the cylinder 117 as compared to a fixed connection between the flexible mount 160 and the piston 130. For example, when the axis of sliding of the piston 130 within the cylinder 117 is angled relative to the axis of reciprocation of the inner back iron 142, the frustoconical surface of the ball head 178 may slide on the ball seat 176 of the piston 130 to reduce friction between the piston 130 and the cylinder 117 relative to the rigid connection between the inner back iron 142 and the piston 130.

The first end 172 of the flexible mount 160 distal from the flexible mount 160 is connected to the inner back iron 142. For example, the flexible mount 160 may be connected to the inner back iron 142 at the 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.

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 a refrigerant or air, through the flexible mount 160 toward the piston head 132 and/or into the piston 130. The inner back iron 142 may be mounted, for example, at an intermediate 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. A passage 192 may extend within the tubular wall 190 between the first end 172 and the second end 174 of the flexible mount 160 such that compressible fluid may 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 way, during operation of the linear compressor 100, compressible fluid may 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 of the compressible fluid flowing through the passage 192.

The piston head 132 also defines at least one opening 196. The opening 196 of the piston head 132 extends through the piston head 132, for example, in the axial direction a. Thus, during operation of the linear compressor 100, fluid may pass through the piston head 132 into the chamber 118 via the opening 196 of the piston head. In this way, fluid (compressed within the chamber 118 by the piston head 132) may flow through the flexible mount 160 and the inner back iron 142 in the channel 192 to the piston 130. As described above, suction valve 128 (fig. 6-7) may be provided on piston head 132 to regulate the flow of compressible fluid through opening 196 into chamber 118.

Still referring to fig. 3-9, a lubrication system 200 that may 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 components of the linear compressor 100 to reduce friction, improve efficiency, and the like. Although lubrication system 200 is described herein with respect to linear compressor 100, it should be appreciated that aspects of lubrication system 200 may be applicable to any other suitable compressor or machine requiring continuous lubrication.

As shown, the housing 102 generally defines a sump 202 configured to collect oil (e.g., as shown herein by reference numeral 204, see fig. 8). Specifically, a sump 202 is defined in the bottom of the lower housing 104. The lubrication system 200 also 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 may include a pump inlet 208, the pump inlet 208 being disposed proximate the bottom of the housing 102 within the sump 202. The pump 206 may draw in the oil 204 from the sump 202 through the pump inlet 208 before circulating the oil 206 through the linear compressor 100, for example, via a supply conduit 210 (fig. 7). Although only one supply conduit 210 is shown in the figures 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 the oil 204 to the various components of the linear compressor 100.

Obviously, according to the illustrated embodiment, the pump inlet 208 is disposed very close to and facing the bottom of the lower housing 104. In this way, the pump 206 can easily suck the oil 204 even when the oil level is low. Specifically, the linear compressor 100 may be configured to receive oil 204 that does not exceed a maximum oil line 212. For example, the maximum fueling line 212 is as shown in fig. 8, and for example, the maximum fueling line may be less than half the distance, or less than one quarter, or lower on the lower case 1. During operation, the pump 206 may circulate the oil 204 throughout the linear compressor 100 prior to recirculation, as will be described in further detail below. Although not illustrated herein, it should be appreciated that lubrication system 200 may include various features, such as various filters, screens, etc., for treating, filtering, or conditioning oil 204 during recirculation. Additionally, it should be appreciated that although the pump 206 is illustrated as being disposed within the sump 202, it may be disposed at any other location and may include a fluid passage that draws the oil 204 from the sump 202.

As also illustrated, the linear compressor 100 may include a suction inlet 220 for receiving a flow of refrigerant. Specifically, suction port 220 may be defined on housing 102 (e.g., such as on lower housing 104) and may be configured to receive a refrigerant supply conduit to provide refrigerant to cavity 108. As described above, the flexible mount 160 includes a tubular wall 190 defining a channel 192 for directing a compressible fluid, such as a refrigerant gas, through the flexible mount 160 toward the piston head 132. Thus, the desired flow path for the refrigerant gas is through suction port 220, through passage 192, through opening 196 and into chamber 118. Suction valve 128 may block opening 196 during a compression stroke and discharge valve 116 may allow compressed gas to exit chamber 118 when a desired pressure is reached.

The flexible mount 160 may also define a channel inlet 222, the channel inlet 222 being disposed proximate the second end 174 of the flexible mount 160 for drawing gas from the suction inlet 220 or the cavity 108 into the channel 192. Specifically, the channel inlet 222 may be an opening in the flexible mount 160 that extends generally in a horizontal plane (the same vertical plane) and that opens toward the suction inlet 220. Specifically, according to the illustrated embodiment, the channel inlet 222 and the suction inlet 220 may be disposed substantially in the same horizontal plane. According to the illustrated embodiment, the suction inlet 220 and the channel inlet 222 are also disposed proximate to the midpoint of the housing 102 along the vertical V. However, it should be appreciated that the suction inlet 220 and the channel inlet 222 may be disposed at any other suitable location within the housing 102 according to alternative embodiments.

Referring now specifically to fig. 6-10, the linear compressor 100 may also include features for draining or dissipating heat that has accumulated in oil or lubricant or elsewhere within the linear compressor 100. Specifically, according to an exemplary embodiment, linear compressor 100 includes a heat dissipating assembly 230 that is disposed within cavity 108 and that facilitates facilitating discharge of thermal energy from within cavity 108 to an exterior of housing 102. Although an exemplary heat dissipating assembly 230 is described herein, it should be understood that various changes and modifications may be made to the heat dissipating assembly 230 while remaining within the scope of the present invention. For purposes of explaining aspects of the present invention, the heat dissipating 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 aspects of heat dissipation assembly 230 may be used in other compressors and other lubrication systems while remaining within the scope of the present invention.

Generally, the heat sink assembly 230 discharges or rejects heat absorbed by the lubricant 204 during operation of the linear compressor 100. In this regard, for example, the thermal lubricant 204 may be transferred directly from the moving components of the linear compressor 100 to the hot oil collection point 232. In this regard, the heat sink assembly 230 may have any suitable mechanism, conduit, or other feature for collecting the lubricant 204 and draining it through the hot oil collection point 232 so that it may be cooled by the heat sink assembly 230, returned to the sump 202, and recycled. For example, according to one exemplary embodiment, a hot oil collection point 232 may be defined on the inner housing 110 for passing the heated lubricant 204 through the inner housing 110.

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

In general, the distribution conduit 240 may be fluidly coupled to any point on the inner shell 110 in any manner or by any mechanism for receiving the heated oil 204. For example, according to the illustrated embodiment, the heat sink assembly 230 includes a supply tube 250 that extends between and provides fluid communication between the hot oil collection point 232 and the fluid inlet 244 of the distribution pipe 240. In this regard, for example, the supply pipe 250 may be a flexible pipe from the hot oil collection point 232 to the distribution pipe 240. According to alternative embodiments, the distribution pipe 240 may 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.

The distribution pipe 240 may generally have any suitable size, location, and configuration for distributing the oil 204 as desired 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 conduit 240 extends around the entire circumference of the housing 102 in a single horizontal plane. More specifically, according to the illustrated embodiment, the distribution conduit 240 is a circular conduit that is directly mounted to the lower housing 104 via a mounting bracket 252. Generally, the mounting bracket 252 is configured to reduce transmission of vibrations from the distribution pipe 240 to the housing 102.

Although the distribution pipe 240 is illustrated as being mounted directly to the lower housing 104, it should be understood that any other suitable mounting location and mechanism may be used according to alternative embodiments. For example, according to an alternative embodiment, the distribution pipe 240 may be mounted directly to the inner housing 110 such that the distribution pipe 240 simply hangs near the housing 102. Alternatively, the distribution conduit 240 may be mounted within the upper housing 106 such that the heated oil 204 drains along a larger surface area of the housing 102 before collecting within the sump 202. Additionally, while the distribution conduit 240 is illustrated as a circular conduit extending in a single horizontal plane, it should be appreciated that the distribution conduit may have any other suitable cross-sectional shape and may pass through the housing in any other suitable pattern or location (e.g., in a serpentine fashion, zigzagged, etc.). Other configurations are possible and within the scope of the invention.

According to an exemplary embodiment, the distribution conduit 240 may be formed of any material having sufficient hardness to maintain the fluid passage and contain the flow of the lubricating oil 204 therein. . For example, according to the illustrated embodiment, the distribution pipe 240 is a small pipe formed of metal. According to alternative embodiments, the distribution conduit 240 may be formed by injection molding, for example using a suitable plastic material such as injection molded grade polybutylene terephthalate (PBT), nylon 6, high Impact Polystyrene (HIPS), perfluoroalkoxy (PFA), fluorinated Ethylene Propylene (FEP), or Acrylonitrile Butadiene Styrene (ABS). Alternatively, according to an exemplary embodiment, these components may be extruded (tubing), compression molded, for example, using Sheet Molding Compound (SMC) thermosets or other thermoplastics. According to other embodiments, the distribution conduit 240 may be formed from any other suitable rigid material.

The discharge ports 246 defined as the distribution conduit 240 may be of any suitable number, shape, size, and configuration to properly direct the flow of heated oil 204 onto 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 pipe 240. According to still other embodiments, the distribution conduit 240 may define an area that does not include the drain 246, e.g., at certain locations where the distribution of the oil 204 may be undesirable, e.g., as near the suction inlet 220.

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

Notably, due to the pressure and flow of the oil 204 within the distribution pipe 240, it may be desirable to restrict the flow, for example, to prevent splashing and/or atomization of the oil 204. Thus, as best shown in fig. 10, the heat sink assembly 230 further includes one or more flow restricting members 270 disposed above the discharge port 246 for restricting the passage of the oil 204 through the discharge port 246. For example, two different flow restricting members 270 are illustrated in FIG. 10. It should be appreciated that these flow restriction members 270 may be used alone or in combination with one another. In particular, the flow restricting member 270 may include a coil spring element 272 that extends around the outer diameter of the dispensing conduit 240 and serves to restrict flow out of the discharge outlet 246. According to an alternative embodiment, the flow restricting member 270 may be a braid or screen 274 disposed over the plurality of discharge ports 246 for restricting flow therethrough. It should be appreciated that any suitable flow restricting member 270 may be used according to alternative embodiments. For example, a cross member or mesh screen may be formed within the orifice 260 during the manufacturing process, or the cross member or mesh screen may be overmolded onto the dispensing conduit 240 after the dispensing conduit is constructed.

The heat dissipating assembly 230 described above may be used to cool the operation of a linear compressor, such as the linear compressor 100 or any other compressor. Specifically, the heat sink assembly 230 may use a mechanism for injecting oil onto the wall of the compressor housing in order to achieve improved heat discharge and compressor efficiency. Specifically, according to an exemplary embodiment, heat dissipation assembly 230 uses a spray mechanism (e.g., distribution pipe 240) to uniformly and in a controlled manner spray oil onto the inner surface of the housing such that heat is conducted to the exterior surface wall. The slow flow of oil within the wall allows the oil to cool.

The distribution pipe 240 operates by receiving hot oil that exits the cylinder under the force of the pump 206. The distribution pipe 240 is provided with a plurality of holes (e.g., discharge ports 246), and the oil is pressed out through the plurality of holes along the outer circumference of the bottom. The oil flows down the wall around the entire lower housing inner wall portion (losing heat to the wall). The slow flowing oil drips down the walls allowing the oil to cool before reaching the sump. The oil remains in liquid form and releases minimal heat to the suction gas inside the shell. The flow of oil may be slowed by the use of porous or flow restricting surfaces (e.g., flow restricting members 270) as the oil flows out of the holes in the pipe. For example, a tight fitting spring may be used to cover the outer diameter of the distribution pipe 240 and provide further flow resistance without atomizing the oil. Instead, similar materials like screens or woven nylon or other polymeric materials may be used to cause oil flow resistance. The flow resistive material allows the oil to flow uniformly down the inner wall (an in-built debris filter is also provided as the oil flows through the sock or spring structure placed over the distribution pipe 240). By starting from the hottest oil at the top of the structure, the oil flows down to the bottom before it is recirculated to the oil pump and compression cylinders and pistons, cooling in the sump, where it again gains heat in a continuous cycle. The present invention provides a low cost method of achieving better efficiency and avoids additional braze joints outside the shell.

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 incorporated 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. Such other examples are intended to be within the scope of the claims if they include structural elements that do not differ from the literal language of the claims, or if they include equivalent structural elements with insubstantial differences from the literal languages of the claims.

Claims

A compressor defining an axial direction and a vertical direction, the compressor comprising:

a housing defining a sump for collecting lubricant;

an inner housing disposed within the housing for receiving a slidable piston, the inner housing defining a hot oil collection point;

a pump for circulating the lubricant within the housing, the pump comprising a pump inlet disposed within the sump; and

a heat dissipating assembly, the heat dissipating assembly 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 discharge ports are provided within the distribution conduit for dripping the lubricant along the housing and back into the sump.
The compressor of claim 1, wherein the plurality of discharge ports are equally spaced along a length of the distribution pipe.
The compressor of claim 1, wherein the plurality of discharge ports includes greater than 50 orifices.
The compressor of claim 1, wherein each of the plurality of discharge ports is disposed and oriented for directing the lubricant onto the inner surface of the housing.
The compressor of claim 1, wherein each of the plurality of discharge ports is defined on a bottom of the distribution pipe.
The compressor of claim 1, wherein each of the plurality of discharge ports is an orifice or a discharge nozzle.
The compressor of claim 1, wherein the heat dissipation assembly further comprises:

a flow restricting member disposed above the plurality of discharge ports for restricting the lubricant from passing through the plurality of discharge ports.
The compressor of claim 7, wherein the flow restricting member is a resilient element extending around the distribution conduit.
The compressor of claim 7, wherein the flow restricting member is a braid or screen disposed over the plurality of discharge ports.
The compressor of claim 1, wherein the distribution conduit extends around an entire circumference of the housing.
The compressor of claim 1, wherein the compressor is a linear compressor.
The compressor of claim 1, wherein the heat dissipation assembly further comprises:

a supply tube providing fluid communication between the hot oil collection point and the fluid inlet of the distribution pipe.
The compressor of claim 1, wherein the distribution conduit is directly attached to the housing.
A heat dissipating assembly for a compressor, the compressor comprising: a housing defining a sump for collecting lubricant; an inner housing disposed within the housing for receiving a slidable piston, the inner housing defining a hot oil collection point; and a pump for circulating the lubricant within the housing, the heat dissipation assembly 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 discharge ports defined within the distribution conduit for dripping the lubricant along the housing and back into the sump.
The heat sink assembly of claim 14 wherein the plurality of discharge openings comprises more than 50 apertures equally spaced along the length of the distribution conduit.
The heat sink assembly of claim 14, wherein each of the plurality of discharge ports is defined on a bottom of the distribution duct.
The heat sink assembly of claim 14, further comprising:

a flow restricting member disposed above the plurality of discharge ports for restricting the lubricant from passing through the plurality of discharge ports.
The heat sink assembly of claim 17, wherein the flow restricting member is a resilient element extending around the distribution conduit or a braid or screen disposed over the plurality of discharge ports.
The heat dissipating assembly of claim 14, wherein said distribution conduit extends around the entire circumference of the lower portion of said housing, and a supply tube provides fluid communication between said hot oil collection point and said fluid inlet of said distribution conduit.
The heat dissipating assembly of claim 14, wherein said compressor is a linear compressor.