KR20230058719A - Heat dissipation assembly of linear compressor - Google Patents

Abstract

The present invention relates to a linear compressor (100) and a heat dissipation assembly (230) thereof. The linear compressor 100 includes a housing 102 in which a storage tank configured to collect lubricant is defined and a pump 206 configured to circulate the lubricant within the housing 102 . It further includes a heat dissipation assembly 230 , which is installed within the cavity 108 and can also promote thermal energy to be dissipated from within the cavity 108 to the outside of the housing 102 . The heat dissipation assembly 230 includes a distribution conduit 240 and a flow restrictor 270, the distribution conduit 240 being connected to a hot oil collection point 232 and also a lubricant 204 along the housing 102. A number of outlets are defined to distribute the lubricant and return the lubricant 204 into the storage tank 202 . The flow restrictor 270 may be installed below the distribution conduit 240 and wrap around the distribution conduit 240 to restrict the flow of the lubricant 204 .

Description

Heat dissipation assembly of linear compressor

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

Some cooling appliances include a sealing system configured to cool the cooling chamber of the cooling appliance. The sealing system usually includes a compressor, which compressor produces compressed refrigerant during operation of the sealing system. The compressed refrigerant flows into the evaporator and, at the location of the evaporator, heat exchange between the cooling chamber and the refrigerant cools the cooling chamber and the food therein. Nowadays, some refrigeration appliances include a linear compressor configured to compress a refrigerant. Linear compressors typically include a piston and drive coil. The drive coil helps create a force that slides the piston forward within the cavity. As the piston moves within the cavity, the piston compresses the coolant.

Typically, an oil or lubricant supply system is included within the compressor housing and is configured to lubricate the piston, thereby reducing frictional force loss as the piston bears against the cavity wall, which negatively affects the efficiency associated with the refrigerant appliance. . However, when the temperature of the oil is high, these linear compressors often suffer from performance problems. For example, if the oil is heated during the operation of the compressor, the oil will atomize or otherwise bounce in all directions, causing mechanical loss in the spring or causing reliability problems such as oil droplets entering the gas inlet together. . Some linear compressors include an external heat exchanger, which transfers the hot oil out of the housing, but such a heat exchanger is complex, expensive, and can easily leak.

Therefore, expectations are high for linear compressors with improved performance characteristics. More particularly, a linear compressor with an oil heat dissipation system is particularly advantageous.

Each aspect and advantage of the present invention is explained in the following description, or becomes apparent through the description, or can be learned by practicing the present invention.

In one exemplary embodiment, a compressor with defined axial and longitudinal directions is provided. The compressor includes a housing defining a storage tank configured to collect lubricant; an inner housing installed within the housing, configured to slidably receive the piston, and defining a hot oil collection point; and a pump configured to circulate the lubricant within the housing and including a pump inlet installed within the storage tank. The heat dissipation assembly includes a distribution conduit extending along an inner surface of the housing, the distribution conduit having a fluid connected to a hot oil collection point and confined within the distribution conduit and a fluid inlet configured to receive lubricant so that the lubricant drips along the housing for storage. A number of outlets configured to return to the tank are defined.

In another exemplary embodiment, a heat dissipation assembly for a compressor is provided. The compressor includes a housing defining a storage tank configured to collect lubricant; an inner housing installed within the housing, configured to slidably receive the piston, and defining a hot oil collection point; and a pump configured to circulate the lubricant within the housing. The heat dissipation assembly includes a distribution conduit extending along an inner surface of the housing, the distribution conduit having a fluid connected to a hot oil collection point and confined within the distribution conduit and a fluid inlet configured to receive lubricant so that the lubricant drips along the housing for storage. A number of outlets configured to return to the tank are defined.

These and other features, aspects and advantages of the present invention may be more readily understood by reference to the following description and appended claims. The drawings, which are incorporated in and constitute a part of this specification, show embodiments of the present invention, and together with the description, allow interpretation of the principles of the present invention.

With reference to the drawings, in the specification, the present invention was completely disclosed to those skilled in the art, and this disclosure enabled those skilled in the art to realize the present invention, and the most preferred of the present invention Include examples.
1 is a front view of a cooling appliance according to an exemplary embodiment of the present invention.
Figure 2 is a schematic diagram of some means of the exemplary cooling appliance of Figure 1;
Fig. 3 is a three-dimensional cross-sectional view of a linear compressor according to an exemplary embodiment of the present invention.
Fig. 4 is another three-dimensional cross-sectional view of the exemplary linear compressor of Fig. 3 according to an exemplary embodiment of the present invention;
Figure 5 is a perspective view of a linear compressor according to an exemplary embodiment of the present invention, wherein the compressor housing has been removed for clarity.
Figure 6 is a cross-sectional view of the exemplary linear compressor of Figure 3 in accordance with an exemplary embodiment of the present invention, wherein the piston is in an extended position;
Figure 7 is a cross-sectional view of the exemplary linear compressor of Figure 3 in accordance with an exemplary embodiment of the present invention, wherein the piston is in a retracted position;
Figure 8 is a schematic cross-sectional view of the exemplary linear compressor of Figure 3 including a heat dissipation assembly in accordance with an exemplary embodiment of the present invention.
Figure 9 is a plan view of the exemplary linear compressor of Figure 3 including the exemplary heat dissipation assembly of Figure 8 in accordance with an exemplary embodiment of the present invention.
Figure 10 is a schematic diagram of some means of the exemplary heat dissipation assembly of Figure 8 in accordance with an exemplary embodiment of the present invention.
Reference numerals are used redundantly in this specification and drawings to indicate the same or similar features or elements of the present invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Reference is now made in detail to embodiments of the present invention, examples of one or several of which are shown in the drawings. Every exemplification is described in such a way as to interpret the invention, and is not intended to limit the invention. In practice, it is obvious to those skilled in the art that various modifications or variations can be made to the present invention without departing from the scope or spirit of the present invention. For example, features shown or described as part of one embodiment may be used on another embodiment, yielding a still further embodiment. Therefore, it is intended that the present invention cover such alterations and modifications as fall within the scope of the appended claims and equivalent forms.

Figure 1 shows a cooling appliance 10 comprising a sealed cooling system 60 (Figure 2). It should be understood that the term “refrigeration appliance” in this context is meant to include any type of cooling appliance, such as freezers, refrigerator/freezer combinations, and traditional refrigerators of any pattern or model. In addition, it should be understood that the present invention is not limited to being used in household appliances. As such, the present invention may be used for any other suitable purpose, for example vapor compression in an air conditioning unit or air compression in an air compressor.

In the exemplary embodiment shown in FIG. 1, the cooling appliance 10 is described as a stand-up refrigerator in a housing body or inner housing 12 defining a plurality of internal cooling storage compartments. In particular, the cooling appliance 10 includes an upper food freshening chamber 14 having a door body 16 and a lower freezing chamber 18 having an upper drawer 20 and a lower drawer 20 . Upper drawer 20 and lower drawer 22 are "pull out" drawers, which can manually pull in and out of freezer compartment 18 on a suitable sliding mechanism.

2 is a schematic diagram of some means of the cooling appliance 10, including a sealed cooling system 60 of the cooling appliance 10. The machine room 62 includes means configured to effect a known cooling air vapor compression cycle. These means include a compressor 64, a condenser 66, an expansion device 68 and an evaporator 70 connected in series and also charged with refrigerant. As will be appreciated by those skilled in the art, refrigeration system 60 may include separate means, for example at least one separate evaporator, compressor, expansion device and/or condenser. Illustratively, the cooling system 60 may include two evaporators.

Within the refrigeration system 60, refrigerant is introduced in a compressor 64, which is operated to increase the pressure of the refrigerant. The compressed refrigerant rises in temperature, which is lowered by passing the refrigerant through the condenser 66. In the condenser 66, the refrigerant and ambient air undergo heat exchange to cool the refrigerant. As illustrated by arrows A _C , fan 72 is used to drive air through condenser 66, providing forced convection and moving faster and faster between the refrigerant in condenser 66 and the surrounding air. This allows for more efficient heat exchange. 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.

Expansion device 68 (eg, a valve, capillary or other restrictor) receives refrigerant supplied from condenser 66 . Refrigerant enters the evaporator 70 from the expansion device 68. As it leaves the expansion device 68 and enters the evaporator 70, the pressure of the refrigerant drops. Due to the pressure drop and phase change of the refrigerant, the evaporator 70 is relatively cold compared to the chambers 14 and 18 of the cold appliance 10 . In this way, cooling air can be generated, and cooling proceeds to the chambers 14 and 18 of the cooling device 10 . Thus, the evaporator 70 is a heat exchanger, and the heat exchanger transfers heat from the air passing through the evaporator 70 to the refrigerant flowing through the evaporator 70 .

In short, the vapor compression circulating means, associated fan, and associated chamber in the refrigeration circuit may in some cases be referred to as a sealed refrigeration system that operates to pass cold air through chambers 14 and 18 (FIG. 1). The cooling system 60 shown in Figure 2 is provided by way of example only. As such, other structures using the cooling system are also within the scope of the present invention.

Referring now collectively to Figures 3-9, a description will be made of a linear compressor 100 according to an exemplary embodiment of the present invention. Specifically, FIGS. 3 and 4 provide an isometric cross-sectional view of the linear compressor 100, FIG. 5 provides a perspective view of the linear compressor 100 with the compressor housing or housing 102 removed for clarity, and FIG. and FIG. 7 provide cross-sectional views of the linear compressor with the piston in the retracted and retracted positions, respectively. It should be understood that the linear compressor 100 herein is merely an exemplary embodiment to facilitate the description of aspects of the present invention. Modifications and changes may be made to the linear compressor 100 while remaining within the scope of the present invention.

For example, as illustrated in FIGS. 3 and 4, housing 102 includes lower housing or lower housing 104 and upper housing or upper housing 106, which are coupled together to form linear compressor 100. forming a generally enclosed cavity 108 configured to receive various means of Specifically, for example, the cavity 108 is a non-breathable or gas-tight housing, which can accommodate the working means of the linear compressor 100, and also allows the refrigerant to leak from the cooling system 60. prevented or prevented from becoming or being exploited. Linear compressor 100 also typically defines an axial direction (A), a radial direction (R) and a circumferential direction (C). It should be understood that linear compressor 100 is only described and illustrated herein to describe aspects of the present invention. Changes and modifications may be made to the linear compressor 100 while remaining within the scope of the present invention.

Referring now to FIGS. 3 to 9 as a whole, various components and working means of the linear compressor 100 according to an exemplary embodiment will be described. As shown in the figure, the linear compressor 100 includes an inner housing 110, the inner housing being between a first end 112 and a second end 114, for example along an axial direction A. can be extended in The inner housing 110 includes an air cylinder 117 in which a cavity 118 is defined. The air cylinder 117 may be installed at or adjacent to the first end 112 of the inner housing 110 . Cavity 118 extends longitudinally along axial direction A. As discussed in more detail below, the linear compressor 100 may be operated to increase the pressure of a fluid within the cavity 118 of the linear compressor 100 . Linear compressor 100 is configured to compress any suitable fluid, such as a cooler or air. Specifically, the linear compressor 100 may be used in a refrigerant appliance, for example, the linear compressor 100 may be used as the refrigerant appliance 10 (FIG. 1) of the compressor 64 (FIG. 2).

The linear compressor 100 includes a stator 120 of a motor in an inner housing 110 . For example, stator 120 typically includes outer bag irons 122 and drive coils 124 extending around circumferential direction C within inner housing 110 . Linear compressor 100 further includes one or more valves, which allow refrigerant to enter or exit cavity 118 during operation of linear compressor 100 . For example, the discharge muffler 126 is installed at one end of the cavity 118 and regulates the flow of the coolant out of the cavity 118, and the intake valve 128 allows the coolant to exit the cavity 118 (for clarity). , only shown in FIGS. 6 to 7).

The piston 130 having the piston head 132 is slidably accommodated in the cavity 118 of the air cylinder 117. Specifically, the piston 130 can slide along the axial direction (A). While the piston head 132 slides within the cavity 118, the piston head 132 compresses the coolant within the cavity 118. As an example, piston head 132 may move from an upper stop position within cavity 118 (eg, see FIG. 6) to a lower stop position along axial direction A (eg, see FIG. 7). ), that is, the expansion stroke of the piston head 132. When the piston head 132 reaches the lower stop position, the piston head 132 changes direction and slides back toward the upper stop position in the cavity 118, that is, the piston head 132 is compressed. refers to administration. It should be understood that the linear compressor 100 may include additional piston heads and/or additional cavities located at the relative ends of the linear compressor 100 . Thus, in an optional exemplary embodiment, the linear compressor 100 may have multiple piston heads.

As illustrated in the figure, linear compressor 100 further includes a rotor 140 configured to compress refrigerant, which is typically driven by stator 120 . Specifically, for example, the rotor 140 may include an inner bag iron 142 installed on the stator 120 of the motor. Specifically, outer bag iron 122 and/or drive coil 124 may extend around inner bag iron 142, for example along circumferential direction C. The inner bag iron 142 further has an outer surface facing the outer bag iron 122 and/or the drive coil 124 . At least one driving magnet 144 is installed on the inner bag iron 142, and may be installed, for example, at a position on the outer surface of the inner bag iron 142.

The drive magnet 144 may face and/or be exposed to the drive coil 124 . Specifically, the drive magnet 144 may be spaced apart from the drive coil 124, for example by one air gap along the radial direction R. This may define an air gap between the relative surfaces of the drive magnet 144 and the drive coil 124 . The drive magnet 144 is installed or fixed to the inner bag iron 142 so that the outer surface of the drive magnet 144 and the outer surface of the inner bag iron 142 are substantially flush with each other. The drive magnet 144 is thereby inserted into the inner bag iron 142 . Then, during the operation of the linear compressor 100, the magnetic field of the drive coil 124 only needs to pass through the single air gap between the outer bag iron 122 and the inner bag iron 142, and both sides of the drive magnet Compared to a linear compressor having an air gap thereon, the linear compressor 100 may have higher efficiency.

As shown in FIG. 3, the drive coil 124 may extend around the inner bag iron 142 along, for example, a circumferential direction C. In another optional exemplary embodiment, the inner bag iron 142 may extend around the drive coil 124 along the circumferential direction (C). The drive coil 124 can be manipulated to cause the inner back iron 142 to move along the axial direction A while the drive coil 124 is operating. As an example, a current source (not shown) reacts with current in the drive coil 124 to generate a magnetic field that draws the drive magnet 144 and also causes the piston 130 to move along the axial direction A. Pushing to move causes the coolant in the cavity 118 to be compressed, as will be understood by those skilled in the art as above. Specifically, while the drive coil 124 is operating, the magnetic field of the drive coil 124 attracts the drive magnet 144, so that the inner back iron 142 and the piston head 132 rotate in the axial direction A. to move along Thus, while the drive coil 124 is operating, the drive coil 124 causes the piston 130 to slide between an upper stop position and a lower stop position, e.g., when the inner back iron 142 is axially Let it move along direction (A).

The linear compressor 100 may include various means configured to permit and/or regulate operation of the linear compressor 100 . Specifically, the linear compressor 100 may include a controller (not shown) configured to regulate operation of the linear compressor 100 . The controller and the motor (eg, the drive coil 124 of the motor) may communicate, for example, in an operational manner. Thus, the controller selectively drives the drive coil 124 through, for example, sensing current among the drive coils 124 to compress the coolant into the piston 130 as described above.

The controller includes a memory and one or more processing units, such as a microprocessor, CPU, etc., such as a general-purpose or special-purpose microprocessor, which microprocessor has programming instructions or microcontrollers associated with the operation of the linear compressor 100. It can be manipulated to execute code. Memory may denote, for example, random access storage such as DRAM or read-only storage such as ROM or FLASH. The processor executes programming instructions stored in memory. The memory may be a separate assembly from the processor or included on a board within the processor. Also optionally, the controller may be a combination of discrete analog and/or digital logic circuits (e.g., switches, amplifiers, integrators, comparators, triggers, AND gates, etc.) ) to build an execution control function, and does not depend on software.

The inner bag iron 142 further includes an outer cylinder 146 and an inner bushing 148. The outer cylinder 146 defines an outer surface of the inner bag iron 142, and further has an inner surface installed relative to the outer surface of the outer cylinder 146. The inner bushing 148 is installed on or at an inner surface location of the outer cylinder 146 . A first clamp fit between the outer cylinder 146 and the inner bushing 148 may connect or secure the outer cylinder 146 and inner bushing 148 together. Also in an optional exemplary embodiment, the inner bushing 148 may be welded, bonded, clamped, or connected to the outer cylinder 146 by any other suitable mechanism or method.

The outer cylinder 146 may be constructed from or using any suitable material. For example, the outer cylinder 146 may be constructed by or using a plurality of laminated plates (eg, composed of magnets). The laminations are distributed along the circumferential direction C to form an outer cylinder 146 and may also be mounted or secured together, for example using rings pressed onto the ends of the laminations. The outer cylinder 146 is defined by a groove, and the groove may extend inwardly from an outer surface of the outer cylinder 146 along a radial direction R, for example. The drive magnet 144 is installed in a recess on the outer cylinder 146 and can, for example, allow the drive magnet 144 to be embedded into the outer cylinder 146 .

The linear compressor 100 further includes a pair of flat springs 150. Each flat spring 150 is coupled to a corresponding end of an inner bag iron 142 along axial direction A, for example. While the drive coil 124 is operating, the flat spring 150 supports the inner bag iron 142. Specifically, the inner bag iron 142 is suspended within the stator or motor of the linear compressor 100 by means of a flat spring 150 to inhibit movement of the inner bag iron 142 along the radial direction R. movement along the axial direction (A) is relatively unimpeded. As such, the flat spring 150 is generally stiffer in the radial direction R than in the axial direction A. Then, while the motor is running and the inner back iron 142 is moving on the axial direction A, the flat spring 150 will move the drive magnet 144 and the drive coil eg along the radial direction R. It is possible to ensure the uniformity of the air gap between (124). The flat spring 150 may also ensure that the lateral traction of the motor is transmitted to the piston 130 and prevents friction losses in the air cylinder 117 .

The elastic installation means 160 is installed on the inner bag iron 142 and extends to pass through the inner bag iron 142. Specifically, the flexible installation means 160 is installed on the inner bag iron 142 via the inner bushing 148. Thus, the flexible installation means 160 is coupled (for example, screwed) to the inner bushing 148 at the middle portion of the inner bushing 148 and/or the flexible installation means 160, so that the flexible installation means ( 160) may be installed or fixed to the inner bushing 148. The flexible installation means 160 may be secured to form the coupling 162 . The coupling 162 may connect the inner back iron 142 and the piston 130 to transfer the movement of the inner back iron 142 to the piston 130 along, for example, an axial direction A.

The coupling 162 may be a flexible coupling having flexibility or elasticity along the radial direction R. Specifically, the coupling 162 has relatively good flexibility along the radial direction R, such that the inner bag iron 142 has little or no movement in the radial direction R, and the coupling 162 has no movement. It can be delivered to the Proston 130 through. In this way, the lateral traction of the motor and the piston 130 and/or the air cylinder 117 are separated, and friction between the piston 130 and the air cylinder 117 can also be reduced.

As shown in the figure, the piston head 132 of the piston 130 has a piston cylindrical sidewall 170 . A corresponding columnar sidewall 170 extends from the piston head 132 towards the inner bag iron 142 along an axial direction A. The outer surface of the cylindrical side wall 170 slides on the air cylinder 117 at the position of the cavity 118, and the inner surface of the cylindrical side wall 170 is relatively positioned with the outer surface of the cylindrical side wall 170. do. Thus, the outer surface of the cylindrical side wall 170 faces the center of the cylindrical side wall 170 along the radial direction R, and the inner surface of the cylindrical side wall 170 along the radial direction R, the cylindrical side wall 170 ) can face the center of

The flexible installation means 160 may extend between the first end 172 and the second end 174 along the axial direction A, for example. According to an exemplary embodiment, a spherical sheet 176 approaching the first end is defined on the inner surface of the cylindrical side wall 170 . Coupling 162 also includes a spherical head 178 . Specifically, for example, the spherical head 178 is installed at the first end 172 of the elastic installation means 160, and the spherical head 178 is installed at the first end 172 of the elasticity installation means 160. In position it contacts the flexible installation means 160 . Also, the spherical head 178 contacts the piston 130 at the position of the spherical seat 176 of the piston 130. Specifically, the spherical head 178 rests on the spherical seat 176 of the piston 130, causing the spherical head 178 to slide and/or rotate on the spherical seat 176 of the piston 130. For example, the spherical head 178 has a spherical surface from which the head is cut closely positioned to the spherical seat 176 of the piston 130, and the spherical seat 176 also has a head of the spherical head 176. may be formed to complement each other with the cut spherical surface. The spherical surface from which the head of the spherical head 178 is cut can slide and/or rotate on the spherical seat 176 of the piston 130 .

For example, compared to a fixed connection between the flexible mounting means 160 and the piston 130, the spherical head 178 and the spherical seat 176 of the piston 130 between the flexible mounting means 160 and the piston 130 ) The relative motion at the interface position between the piston 130 and the air cylinder 117 can reduce the frictional force. For example, if the axis along which the piston 130 slides in the air cylinder 117 is at an angle to the axis of the reciprocating motion of the inner back iron 142, the spherical surface on which the head of the spherical head 178 is cut The silver may slide on the spherical seat 176 of the piston 130, reducing friction between the piston 130 and the air cylinder 117 against the rigid connection between the inner back iron 142 and the piston 130. .

The flexible installation means 160 is connected to the inner bag iron 142 away from the first end 172 of the flexible installation means 160 . For example, the flexible installation means 160 is connected to the inner bag iron 142 between the second end 174 of the elastic installation means 160 or between the first and second ends of the elastic installation means 160. do. Conversely, the flexible installation means 160 is positioned at or within the piston 130 at the location of the first end 172 of the flexible installation means 160, as discussed in more detail below.

Furthermore, the flexible installation means 160 comprises a tubular wall 190 between the inner bag iron 142 and the piston 130, the passage 192 in the tubular wall 190 being for example compression of a coolant or air. It is configured to guide possible fluid through the flexible mounting means 160 to the piston head 132 and/or into the piston 130 . The inner bag iron 142 is installed, for example, at a position in the middle of the elastic installation means 160 between the first end 172 and the second end 174 of the elasticity installation means 160, and the inner bag iron ( 142 surrounds and extends around the tubular wall 190 . A passage 192 extends within the tubular wall 190 between the first end 172 and the second end 174 of the flexible installation means 160 so that a compressible fluid passes through the passage 192 for a flexible installation. It flows from the first end 172 of the means 160 to the second end 174 of the flexible installation means 160. In this case, during operation of the linear compressor 100, the compressible fluid may pass through the inner bag iron 142 in the flexible installation means 160. Silencer 194 may be installed within passage 192 in tubular wall 190 and attenuate, for example, the noise of a compressible fluid passing through passage 192 .

Piston head 132 further defines at least one opening 196 . The opening 196 of the piston head 132 extends along the axial direction A, for example, and passes through the piston head 132 . Thus, during operation of the linear compressor 100, fluid passes through the piston head 132 via the opening 196 in the piston head and arrives in the cavity 118. When this happens, the fluid (compressed by the piston head 132 within the cavity 118) passes through the flexible installation means 160 and the inner bag iron 142 and flows out of the passage 192 to the piston 130. As noted above, an intake valve 128 (FIGS. 6-7) is installed on the piston head 132 to regulate the flow rate of the compressible fluid through the opening 196 into the cavity 118. .

Still referring to FIGS. 3-9 , a lubrication system 200 usable with the linear compressor 100 is described. Specifically, the lubrication system 200 may be configured as a moving means or an operation for cyclically passing a lubricant such as oil, for example, through the linear compressor 100, thereby reducing friction and improving efficiency. . Although lubrication system 200 has been described herein with respect to linear compressor 100, it should be understood that aspects of lubrication system 200 may be applied to any other suitable compressor or machine requiring continuous lubrication.

As shown in the figure, housing 102 typically defines a storage tank 202, which is configured to collect oil (e.g., as shown at figure 204 in the text, FIG. see 8). Specifically, the storage tank 202 is defined in the lower portion of the lower housing 104 . The lubrication system 200 further comprises a pump 206, which pump is configured to continuously circulate oil 204 through the means for lubrication of the linear compressor 100. In this regard, for example, the pump 206 includes a pump inlet 208, which is installed to access the bottom of the housing 102 within the storage tank 202. Before oil 204 circulates through linear compressor 100, for example via supply conduit 210 (FIG. 7), pump 206 passes through pump inlet 208 to storage tank 202. oil 204 is sucked from For clarity, only one supply conduit 210 is shown in the drawings, but it should be understood that the lubrication system 200 may include any suitable number of supply conduits, nozzles, and other dispensing features. To provide oil 204 to each unit of compressor 100.

Significantly, according to the illustrated embodiment, the pump inlet 208 is installed very close to and facing the bottom of the lower housing 104 . In this case, even when the oil level is low, the pump 206 can easily suck in the oil 204. Specifically, the linear compressor (100) is configured to receive oil (204) that does not exceed a maximum oil addition line (212). For example, the maximum oil addition line 212 is as shown in FIG. 8, and for example, the maximum oil addition line is less than half the distance on the lower housing 1, or less than a quarter of the distance. It may be in a lower position, or even lower. During operation, pump 206 causes oil 204 to circulate in first half linear compressor 100 before recirculation, as described in further detail below. Although not illustrated herein, it should be understood that the lubrication system 200 may include features configured to treat, filter, or condition the oil 204 during recirculation, such as various filters, meshes, and the like. It should also be understood that the pump 206 is illustrated to be installed within the storage tank 202, but it may be installed in any other location, and also the fluid passageway that draws the oil 204 from the storage tank 202. can include

As also illustrated in the figures, the linear compressor 100 includes an intake 220 configured to receive a flow of refrigerant. Specifically, the inlet 220 is defined on the housing 102 (eg, on the lower housing 104) and is configured as a supply conduit to receive coolant and provide coolant to the cavity 108. . As noted above, the flexible mounting means 160 comprises a tubular wall 190, which defines a passageway 192, which passage can pass a compressible fluid, for example a coolant gas, into the flexible mounting means. It is configured to guide through 160 to piston head 132 . If this is so, the desired flow path for the coolant gas is through intake 220 , through passage 192 , through opening 196 , and into cavity 118 . The intake valve 128 closes the opening 196 during the compression stroke, and the discharge valve 116 allows compressed gas to exit the cavity 118 when the desired pressure is reached.

The flexible installation means 160 further defines a passage inlet 222, and the passage inlet 222 is installed to approach the second end 174 of the flexible installation means 160, and the gas inlet 220 or It is configured to suck in from the cavity 108 and enter the passage 192 . Specifically, the passage inlet 222 may be an opening on the flexible installation means 160, the opening extending in a substantially horizontal plane (the same vertical plane) and the opening facing the suction port 220. Specifically, according to the illustrated embodiment, the passage inlet 222 and the inlet 220 are installed in substantially the same horizontal plane. According to the illustrated embodiment, the inlet 220 and the passage inlet 222 are also installed to approach the center of the housing 102 along the longitudinal direction V. However, it should be understood that, according to alternative implementations, the inlet 220 and passage inlet 222 may be located in any other suitable location within the housing 102 .

Referring now specifically to FIGS. 6-10 , the linear compressor 100 may further include features configured to discharge or dissipate the amount of heat accumulated in or other portions of oil or lubricant already within the linear compressor 100 . there is. Specifically, according to an exemplary embodiment, the linear compressor 100 includes a heat dissipation assembly 230, which is installed within the cavity 108 and transfers thermal energy from the cavity 108 to the outside of the housing 102. promote discharge. Although an exemplary heat dissipation assembly 230 has been described herein, it should be understood that various changes and modifications may be made to the heat dissipation assembly 230 while remaining within the scope of the present invention. For purposes of interpreting aspects of the present invention, the heat dissipation assembly 230 is described below for use with the lubrication system 200 of the linear compressor 100. However, it should be understood that each aspect of the heat dissipation assembly 230 may be used with other compressors and other lubricating systems, as long as it remains within the scope of the present invention.

Typically, heat dissipation assembly 230 discharges or discharges the amount of heat absorbed by lubricant 204 during operation of linear compressor 100 . For example, hot lubricant 204 is delivered directly from the moving means of linear compressor 100 to hot oil collection point 232. In this regard, the heat dissipation assembly 230 may include any suitable mechanism, conduit, or other feature configured to collect the lubricant 204 and drain it through the hot oil collection point 232 to thereby dissipate heat. Cooled by assembly 230, returned to storage tank 202 and also recycled. For example, according to one exemplary embodiment, a hot oil collection point 232 is defined on the inner housing 110 and allows heated lubricant 204 to pass from the inner housing 110 .

As most preferably shown in FIGS. 6-10 , the heat dissipation 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 that is fluidly coupled to a hot oil collection point 232 on the inner housing 110 . The distribution conduit also defines a plurality of outlets 236, which outlets 246 are configured to spray, drip, or otherwise deposit lubricant 204 along housing 102, thereby distributing the lubricant to pump 206. ) to be collected again in the storage tank 202 before recycling. In this way, the oil 204 is propelled through the working means of the linear compressor 100, minimizing friction and improving working efficiency, and the oil absorbs heat during the process. The heated oil 204 then exits the inner housing 110 through a hot oil collection point 232 where it is distributed within a distribution conduit 240 and surrounding the housing 102 . The heated oil 204 is then sprayed onto the housing 102 where the temperature is lower than the heated oil 204 . When the heated oil 204 flows down from the housing 102 and is again collected in the storage tank 202, thermal energy is transferred from the oil 204 to the housing 102, and in the housing, the thermal energy is released into the surrounding environment. . This allows the oil 204 to be recycled at relatively cool temperatures, thereby improving the performance and life of the linear compressor 100.

Typically, the distribution conduit 240 is fluidly coupled in any manner or via any mechanism to any point on the inner housing 110 and is configured to receive the heated oil 204 . For example, according to the illustrated embodiment, the heat dissipation assembly 230 includes a supply tube 250 that extends between the hot oil collection point 232 and the fluid inlet 244 of the distribution conduit 240. and provide fluid communication between them. In this regard, for example, supply conduit 250 may be a flexible conduit from hot oil collection point 232 to distribution conduit 240 . According to an optional implementation, the distribution conduit 240 is coupled directly to the inner housing, for example through the hot oil collection point 232 or through any other outlet of the inner housing 110 .

Distribution conduit 240 can typically be of any suitable size, location and configuration for dispensing oil 204 on demand to ensure operation of heat dissipation assembly 230 and cooling of linear compressor 100. there is. For example, according to the illustrated implementation, distribution conduit 240 extends around the entire circumference of housing 102 in a single horizontal plane. More specifically, according to the exemplified implementation, the distribution conduit 240 is a circular conduit that passes through the mounting bracket 252 and is directly installed on the lower housing 104 . Typically, the mounting bracket 252 is configured to reduce vibration transmission from the distribution conduit 240 onto the housing 102 .

Distribution conduit 240 is illustrated to be installed directly into lower housing 104, but it should be understood that any other suitable installation location and mechanism may be used, depending on the alternative implementation. For example, according to an optional implementation, the distribution conduit 240 can be mounted directly to the inner housing 110, making it simple to suspend the distribution conduit 240 proximate to the housing 102. Optionally, distribution conduit 240 can be installed within upper housing 106 and will allow heated oil 204 to drain along a relatively large area of housing 102 before being collected in storage tank 202. can Further, while distribution conduit 240 is illustrated as a circular conduit extending in a single horizontal plane, it should be understood that the distribution conduit may have any other suitable cross-sectional shape, as well as any other suitable pattern or location (eg, , meandering, zigzag, etc.) through the housing. Other arrangements are possible and within the scope of the present invention.

According to an exemplary embodiment, the distribution conduit 240 can be formed from any material that has sufficient hardness to maintain a fluid passageway and accommodate the flow of lubricant 204 therein. . For example, according to the illustrated implementation, distribution conduit 240 may be a small conduit formed of metal. According to an optional implementation, the distribution conduit 240 is plastic injection, for example, a suitable plastic material (eg, plastic injection grade polybutylene terephthalate (PBT), nylon 6, high-impact polystyrene (HIPS), perfluoroalkoxy (PFA), fluoroethylene propylene (FEP) or acrylonitrilebutadiene styrene (ABS)). Optionally, according to an exemplary embodiment, such means is extruded (conduit) and compression molded using, for example, a sheet molding compound (SMC) thermoset or other thermoplastic. According to some other embodiments, distribution conduit 240 may be formed of any other suitable rigid material.

The outlets 246 of the distribution conduit 240 may be of any suitable quantity, shape, size, and configuration, and suitably direct the flow of heated oil 204 onto a desired portion of the housing 102. For example, according to the illustrated implementation, the number of outlets 246 is greater than 10, greater than 25, greater than 50, or greater than 10 equally spaced apart along the length of the distribution conduit 240. It includes a number of outlets 246 greater than 75 or greater than 100. In addition, according to other technical means, the distribution conduit 240 is limited to a region that does not include the outlet 246, for example, some locations where the distribution of the oil 204 is not ideal, for example, the gas inlet It refers to a position approaching 220.

According to an exemplary embodiment, outlet 246 is a simple hole 260 drilled, machined, punched, or otherwise formed in distribution conduit 240 . According to some other embodiments, each outlet 246 includes a discharge nozzle, and the discharge nozzle is installed above the hole 260 to selectively control the flow rate and direction of the oil 204 . According to the illustrated implementation, an outlet 246 (eg, hole 260 ) is defined on the underside 262 of the distribution conduit 240 . However, according to alternative implementations, outlet 246 is defined on the side, top, or on any suitable location along distribution conduit 240 . For example, outlet 246 is angled downward along the longitudinal direction and away from the vertical centerline of linear compressor 100 . When this is done, the oil 204 is propelled directly towards the lower housing 104 and also down into the storage tank 202 . According to some other embodiments, the outlet 246 is installed and directed in any other suitable manner to guide the oil 204 onto the inner surface 242 of the housing 102 .

It should be noted that due to the pressure and flow of oil 204 in distribution conduit 240, it may be desirable to restrict the flow, for example, to prevent oil 204 from splashing and/or atomizing. there is. Thus, as most appropriately shown in FIG. 10, the heat dissipation assembly 230 further includes one or more flow restricting means 270, and these flow restricting means are installed above the outlet 246 so that the oil ( 204) is configured to restrict passage through outlet 246. For example, in Fig. 10 two different flow restricting means 270 are illustrated. It should be understood that these flow restrictors 270 may be used alone or in combination with each other. Specifically, the flow restricting means 270 comprises a coil spring element 272, which coil spring element extends around the outer diameter of the distribution conduit 240 and restricts the flow out of the outlet 246. It consists of According to an optional implementation, the flow restrictor 270 may be a knitted fabric or mesh 274 installed over the plurality of outlets 246 and configured to restrict flow through them. It should be understood that any suitable flow restricting means 270 may be used, depending on the possible implementations. For example, in the manufacturing process, the transverse means or mesh may be formed in the hole 260, or after the distribution conduit is manufactured, the transverse means or mesh may be wrapped and formed on the distribution conduit 240.

The heat dissipation assembly 230 may be used in the operation of cooling a linear compressor (eg, linear compressor 100 or any other compressor). Specifically, the heat dissipation assembly 230 may use a mechanism to spread oil onto the walls of the compressor housing, thereby achieving improved heat dissipation and compressor efficiency. Specifically, according to an exemplary embodiment, the heat dissipation assembly 230 sprays oil on the inner surface of the housing in a uniform and controllable manner using a spraying mechanism (eg, the distribution conduit 240) to reduce the amount of heat. to be transmitted to the outer surface wall. Allowing the oil to cool by allowing the oil to flow slowly within the walls.

Distribution conduit 240 works by receiving hot oil from the air cylinder by the action of pump 206. The distribution conduit 240 is provided with a number of holes (e.g., outlets 246), and oil is extruded through the number of holes along the bottom circumference. The oil flows down the entire lower housing inner wall along the wall (heat is lost in the wall). Slowly flowing oil drips down the walls, allowing the oil to cool before reaching the storage tank. The oil remains in liquid form and releases the least amount of heat towards the suction gas inside the housing. As oil exits the hole in the conduit, the flow of oil is decelerated through the use of multiple holes or flow restricting surfaces (eg, flow restricting means 270). For example, press-fit springs can be used to cover the outer diameter of the distribution conduit 240 and also provide further flow resistance under circumstances that will prevent the oil from atomizing. Conversely, a mesh or similar material such as knitted nylon or other polymeric material is used to resist the flow of oil. The flow resistant material allows the oil to flow uniformly down the inner wall (when the oil is via a sock or spring structure disposed on the distribution conduit 240, it further provides one built-in debris filter). Starting with the hottest oil at the top of the structure, the oil flows down to the bottom before being recirculated to the oil pump, compressed air cylinder and piston, where it is cooled in a storage tank, and the oil is then circulated to the oil pump, compressed air cylinder in successive circulations. and gain heat again at the piston position. The present invention provides a low cost method of achieving greater efficiency and also avoids a separate solder joint outside the housing.

The description of the present invention proceeds by way of example to disclose the present invention (herein including the best mode), and also allows those skilled in the art to make and use the present invention (herein any apparatus or system including, and included in any The method of) was made possible. The patent scope of the present invention is defined by the claims, and may also include other examples conceived by those skilled in the art. If these other examples include structural elements with no difference from the description in the claims, or if these other examples include equivalent structural elements with no material differences from the description in the claims, then these other examples are within the scope of the claims. Must be within range.

Claims (20)

compressor,
a housing defining a storage tank configured to collect the lubricant;
an inner housing installed within the housing, configured to slidably receive the piston, and defining a hot oil collection point;
a pump configured to circulate the lubricant inside the housing and including a pump inlet installed in the storage tank; and
A heat dissipation assembly; including, the heat dissipation assembly,
a distribution conduit extending along an inner surface of the housing, defining a fluid inlet, the fluid inlet being fluidly connected to the hot oil collection point and configured to receive the lubricant; and
and a plurality of outlets installed within the distribution conduit and configured to allow the lubricant to drip down the housing and back into the storage tank. According to claim 1,
Compressor, characterized in that the plurality of outlets are spaced at the same distance along the longitudinal direction of the distribution conduit. According to claim 1,
Compressor, characterized in that the plurality of outlets include a number of holes greater than 50. According to claim 1,
Each outlet of the plurality of outlets is provided and directed to guide the lubricant onto the inner surface of the housing. According to claim 1,
wherein each outlet of said plurality of outlets is defined on a bottom of said distribution conduit. According to claim 1,
Compressor, characterized in that each outlet of the plurality of outlets is a hole hole or a discharge nozzle. According to claim 1,
The heat dissipation assembly,
The compressor according to claim 1 , further comprising flow restricting means, the flow restricting means being installed above the outlets and configured to restrict the lubricant from passing through the plurality of outlets. According to claim 7,
The compressor of claim 1, wherein the flow restricting means is an elastic element extending around the distribution conduit. According to claim 7,
The compressor according to claim 1, wherein the flow restriction means is a knitted fabric or mesh provided above the plurality of outlets. According to claim 1,
The compressor of claim 1 , wherein the distribution conduit extends around the entire circumference of the housing. According to claim 1,
Compressor, characterized in that the compressor is a linear compressor. According to claim 1,
The heat dissipation assembly,
The compressor of claim 1 further comprising a supply line, the supply line providing fluid communication between the hot oil collection point and the fluid inlet of the distribution conduit. According to claim 1,
The compressor of claim 1 , wherein the distribution conduit is directly attached to the housing. The compressor includes a housing defining a storage tank configured to collect lubricant; an inner housing installed within the housing, configured to slidably receive the piston, and defining a hot oil collection point; and a pump configured to circulate the lubricant within the housing. Including, the heat dissipation assembly,
a distribution conduit extending along an inner surface of the housing, defining a fluid inlet, the fluid inlet being fluidly connected to the hot oil collection point and configured to receive the lubricant; and
and a plurality of outlets defined within the distribution conduit and configured to allow the lubricant to drip down the housing and back into the storage tank. According to claim 14,
The heat dissipation assembly, characterized in that the plurality of outlets include a number of holes greater than 50 spaced at equal distances along the longitudinal direction of the distribution conduit. According to claim 14,
wherein each outlet of the plurality of outlets is defined on a bottom of the distribution conduit. According to claim 14,
The heat dissipation assembly further comprising a flow restricting means, wherein the flow restricting means is installed above the plurality of outlets to restrict the lubricant from passing through the plurality of outlets. According to claim 17,
The heat dissipation assembly, characterized in that the flow restrictor is an elastic element extending around the distribution conduit or a knitted fabric or mesh installed above the plurality of outlets. According to claim 14,
wherein the distribution conduit extends around the entire circumference of the lower portion of the housing, and wherein a supply conduit provides fluid communication between the hot oil collection point and the fluid inlet of the distribution conduit. According to claim 14,
The heat dissipation assembly, characterized in that the compressor is a linear compressor.

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