Linear compressor and refrigeration equipment

Abstract

The invention discloses a linear compressor and refrigeration equipment, and the linear compressor comprises a shell, a frame body arranged in the shell, a piston cylinder arranged on the frame body, a piston assembly and a driving unit; the piston cylinder is provided with a cylinder body and a piston cavity penetrating through the cylinder body, the piston assembly comprises a piston, and the driving unit drives the piston to reciprocate in the piston cavity; the piston is provided with a piston air inlet channel communicated with the piston cavity, the piston assembly is provided with a support cavity communicated with the piston air inlet channel and a silencing structure arranged in the support cavity, the silencing structure comprises a silencing pipe with a flowing channel, and the position, close to the piston, of the silencing pipe is provided with a flowing outlet exposed towards the support cavity. And the opening direction of the flowing outlet is obliquely crossed with the axial direction of the piston. The high noise generated in the transmission process of a refrigerant can be effectively reduced.

Description

Technical Field

[0001] The invention relates to the technical field of linear compressors, in particular to linear compressors and refrigeration equipment. Background Art

[0002] A linear compressor is a mechanical device that compresses air, refrigerant or other various working gases and increases their pressure by receiving power from a power generating device such as a motor or a turbine. Linear compressors are widely used in household appliances such as refrigerators and air conditioners or in the entire industrial field.

[0003] As a type of linear compressor, the linear compressor controls the movement of the piston through a linear reciprocating drive motor. Compared with the non-linear compressor, it does not require motion conversion, thus avoiding the mechanical loss caused by operation conversion, which can improve the compression efficiency and simplify the overall structure.

[0004] In a linear compressor, the piston reciprocates linearly in the piston cylinder to compress the refrigerant entering the compression space; the refrigerant will generate relatively large noise during the flow process. In order to reduce the noise, the linear compressor also includes a silencer structure. The silencer effect of the silencer structure in the prior art is not significant enough. Summary of the invention

[0005] The purpose of the present invention is to provide a linear compressor to solve the deficiencies in the prior art, which can effectively reduce the loud noise generated during the transmission of refrigerant.

[0006] The linear compressor provided by the present invention comprises: a housing, a frame arranged in the housing, a piston cylinder arranged on the frame, a piston assembly and a driving unit;

[0007] The piston cylinder has a cylinder body and a piston cavity penetrating the cylinder body, the piston assembly includes a piston, and the driving unit drives the piston to reciprocate in the piston cavity;

[0008] The piston is provided with a piston air inlet channel connected to the piston cavity, the piston assembly has a bracket cavity connected to the piston air inlet channel and a silencer structure provided in the bracket cavity, the silencer structure includes a silencer pipe with a flow channel, the silencer pipe has a flow outlet exposed toward the bracket cavity at a position close to the piston, and the opening direction of the flow outlet is oblique to the axial direction of the piston.

[0009] Furthermore, the opening direction of the flow outlet is perpendicular to the axial direction of the piston.

[0010] Furthermore, the flow outlet is provided in plurality, and the plurality of flow outlets are arranged along the circumferential direction of the muffler pipe.

[0011] Furthermore, the muffler pipe comprises a pipe body having a pipe cavity, a baffle and a baffle support column;

[0012] The tube body is extended in a direction parallel to the axial direction of the piston and has a proximal end and a distal end that are arranged opposite to each other, and the proximal end of the tube body is closer to the piston than the distal end; the baffle is fixed to the proximal end of the tube body by the baffle support and the baffle is opposite to the lumen;

[0013] The flow outlet is arranged between the baffle and the tube body.

[0014] Furthermore, two baffle support columns are provided, and two flow outlets arranged opposite to each other are formed between the two baffle support columns.

[0015] Furthermore, the silencer pipe includes a pipe body and a plurality of partition plates arranged on the outer wall of the pipe body, the plurality of partition plates are arranged along the axial direction of the pipe body, the partition plates are attached to the inner wall of the piston bracket, a silencer cavity is formed between two adjacent partition plates, and a pipe body through hole connecting the flow channel and the silencer cavity is arranged on the pipe body.

[0016] Furthermore, as the distance from the piston increases, the outer diameter of the piston support gradually increases, and the outer diameter of the tube body also gradually increases.

[0017] Furthermore, the compressor also has an air release component, which includes an air release valve plate arranged on one side of the cylinder body and used to open or close the piston chamber; a working chamber is formed between the piston and the air release valve plate, and the driving unit drives the piston to reciprocate in the piston chamber to increase or compress the working chamber;

[0018] The piston assembly further comprises a piston valve plate, which moves on the piston to control the connection or closing of the piston air inlet passage and the working chamber.

[0019] Furthermore, the driving unit includes a stator assembly and a mover assembly, and the mover assembly drives the piston to reciprocate in the piston cylinder;

[0020] The stator assembly is disposed on the frame and cooperates with the mover assembly to drive the mover assembly to move;

[0021] The mover frame comprises an inner guard iron and a driving magnet arranged on the outer wall of the inner guard iron, wherein the driving magnet is arranged in an annular shape on the outer wall of the inner guard iron to form a driving magnet ring;

[0022] The stator assembly includes a stator frame and a driving coil arranged on the stator frame, and the stator frame is fixed on the frame; the driving coil is opposite to the driving magnet and is arranged around the driving magnet to form a driving coil ring, and the driving coil ring is coaxially arranged with the driving magnet ring; the electromagnetic force generated by the driving coil after being energized drives the driving magnet to reciprocate along the axial direction of the piston.

[0023] Another embodiment of the present invention further discloses a refrigeration device, including a box body and a refrigeration system arranged on the box body, wherein the refrigeration system includes the linear compressor.

[0024] Compared with the prior art, the opening direction of the flow outlet of the circulation channel in the silencer structure of the present invention is not along the axial direction of the piston, which can avoid affecting the piston valve plate on the piston. At the same time, since the entire flow channel of the refrigerant has added a certain degree of bending, the flow velocity can be buffered and the loud noise generated by the refrigerant during the transmission process can be effectively reduced. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] Figure 1 It is a schematic diagram of the installation structure of the linear compressor disclosed in the embodiment of the present invention in the housing;

[0026] Figure 2 yes Figure 1 A top view of

[0027] Figure 3 yes Figure 2 Sectional view in the AA direction;

[0028] Figure 4 yes Figure 3 A partial enlarged view of point B in the middle;

[0029] Figure 5 is a schematic diagram of a first internal structure of the linear compressor disclosed in an embodiment of the present invention after the outer shell is removed;

[0030] Figure 6 is a schematic diagram of a second internal structure of the linear compressor disclosed in an embodiment of the present invention after the outer shell is removed;

[0031] Figure 7 It is a structural schematic diagram of a piston assembly in a linear compressor disclosed in an embodiment of the present invention;

[0032] Figure 8 yes Figure 7 Cross-sectional view in CC direction;

[0033] Fig. 9 is a three-dimensional diagram of a piston assembly in a linear compressor disclosed in an embodiment of the present invention;

[0034] Fig.10It is a structural schematic diagram of the piston assembly in the linear compressor disclosed in an embodiment of the present invention after the piston is unloaded;

[0035] Fig.11 It is a structural schematic diagram of the piston assembly in the linear compressor disclosed in the embodiment of the present invention after the piston and the ball head structure are unloaded;

[0036] Fig.12 It is a first structural schematic diagram of a piston in a linear compressor disclosed in an embodiment of the present invention;

[0037] Fig.13 is a second structural schematic diagram of a piston in a linear compressor disclosed in an embodiment of the present invention;

[0038] Fig.14 It is a structural schematic diagram of a ball head support member in a linear compressor disclosed in an embodiment of the present invention;

[0039] Fig.15 is a first structural schematic diagram of a muffler structure in a linear compressor disclosed in an embodiment of the present invention;

[0040] Fig.16 is a second structural schematic diagram of the muffler structure in the linear compressor disclosed in an embodiment of the present invention;

[0041] Fig.17 It is a front view of the muffler structure in the linear compressor disclosed in the embodiment of the present invention;

[0042] Description of reference numerals: 1-housing, 10-accommodating cavity, 11-elastic supporting leg,

[0043] 2-frame, 21-annular fixing frame, 22-locking piece, 221-locking screw, 222-locking nut,

[0044] 3-piston cylinder, 31-cylinder body, 32-piston chamber,

[0045] 4-piston assembly, 41-piston, 411-converging groove, 412-air inlet, 4121-first hole body, 4122-second hole body, 413-valve plate mounting column, 414-hemispherical depression, 415-fastener connecting column,

[0046] 42-piston bracket, 420-bracket cavity, 4201-buffer cavity, 421-bracket body, 4211-bracket positioning groove, 4212-positioning piece, 422-external thread connection part, 424-ball head structure, 4241-ball head positioning hole, 425-ball head support, 4251-annular positioning part, 4252-ball head combining ring,

[0047] 43-piston valve plate, 431-valve plate body, 432-installation plate, 433-connecting plate,

[0048] 44-fastening structure, 441-fastening support plate, 442-fastener, 443-compression spring,

[0049] 5-motor assembly, 50-motor through hole, 51-motor frame, 511-inner guard iron, 5111-inner guard iron avoidance groove, 5112-inner guard iron protrusion, 512-annular mounting piece, 5121-first annular mounting piece, 5122-second annular mounting piece,

[0050] 514-internal thread connection,

[0051] 52-driving magnet,

[0052] 6- stator assembly, 61- stator frame,

[0053] 7-silencing structure, 70-flow channel, 701-flow inlet, 702-flow outlet, 71-silencing pipe, 711-tube body, 7111-installation section, 7112-extension section, 712-tube body through hole, 72-partition plate, 73-silencing chamber, 74-blocking plate, 75-blocking plate support column,

[0054] 8-connecting assembly, 81-elastic member, 811-fixed end, 812-free end,

[0055] 9-oil pump system, 90-oil inlet channel, 91-oil pump, 911-oil pump housing, 912-oil pump piston, 913-oil outlet pipe, 92-oil suction pipe. DETAILED DESCRIPTION

[0056] Embodiments of the present invention are described in detail below, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended to be used to explain the present invention, and should not be construed as limiting the present invention.

[0057] An embodiment of the present invention discloses a linear compressor, which is used in a refrigeration device as a part of a refrigeration system. The linear compressor is connected between an evaporator and a condenser to compress the refrigerant coming out of the evaporator into a high-temperature and high-pressure gas, which then enters the condenser for cooling.

[0058] It should be understood that the term "refrigeration equipment" is used herein in a general sense to cover any manner of refrigeration appliance, such as a freezer, a refrigerator, a freezer, a freezer combination, and any style or model of conventional refrigerator. In addition, it should be understood that the subject matter is not limited to use in refrigeration appliances. Therefore, the subject matter can be used for any other suitable purpose, such as vapor compression in an air conditioning unit or air compression in an air linear compressor.

[0059] The refrigeration device is a refrigerator, which includes a box body, a plurality of refrigeration compartments arranged on the box body, and a door body arranged on the box body and opening or closing the refrigeration compartments. The refrigeration device also has a refrigeration system arranged on the box body, and the refrigeration system includes a linear compressor, a condenser, a throttling device, an evaporator and a refrigerant filled in the circulation loop, which are connected in sequence to form a circulation loop.

[0060] The refrigerant in the refrigeration system flows into the linear compressor, which can increase the pressure of the refrigerant. After being compressed by the linear compressor, the refrigerant will increase its temperature to form a high-temperature and high-pressure gas. After the refrigerant flows out of the linear compressor, it passes through the condenser to reduce the temperature. The refrigerant exchanges heat with the ambient air in the condenser, thereby cooling the refrigerant.

[0061] The linear compressor disclosed in this embodiment can be operated to increase the fluid pressure in the chamber, and the linear compressor can be used to compress any suitable fluid, such as refrigerant or air. In particular, the linear compressor can be used as a linear compressor for refrigeration equipment.

[0062] like Figure 1-4 As shown, the linear compressor includes a sealed housing 1, which can prevent or block the refrigerant from leaking or escaping from the refrigeration system. Other components of the linear compressor are packaged in the sealed housing 1. The housing 1 has a receiving cavity 10. It should be noted that, in order to facilitate understanding of the embodiment, the housing 1 is provided with a plurality of housings, each of which ... Figure 1 A schematic diagram of the structure of the upper shell of the housing 1 after unloading is given.

[0063] The linear compressor further comprises a frame 2, a piston cylinder 3 disposed on the frame 2, a piston assembly 4 and a driving unit; the frame 2, the piston cylinder 3 disposed on the frame 2, the piston assembly 4 and the driving unit are all disposed in the accommodating chamber 10;

[0064] like Figure 3 As shown, the piston cylinder 3 includes a cylinder body 31 and a piston cavity 32 penetrating the cylinder body 31, the cylinder body 31 is fixed on the frame 2, and the piston assembly 4 includes a piston 41, the piston 41 slides in the piston cavity 32, and the piston 41 is cylindrical as a whole and has an axial direction. The driving unit drives the piston 41 to reciprocate in the piston cavity 32, and the piston 41 moves along its axial direction, and the refrigerant in the piston cavity 32 is sucked and squeezed during the reciprocating movement of the piston 41.

[0065] The piston 41 is provided with a piston inlet passage, through which the refrigerant enters the piston chamber 32 to be squeezed by the piston 41 during the reciprocating movement. The piston assembly also has a piston valve plate 43, which moves on the piston 41 to control the opening or closing of the piston inlet passage and the piston chamber 32.

[0066] It can be understood that the linear compressor also has a relief assembly (not shown), which includes a relief valve plate arranged on one side of the cylinder body 31 and used to open or close the piston chamber 32; a working chamber is formed between the piston 41 and the relief valve plate, and the refrigerant is introduced into the working chamber and compressed in the working chamber. The space of the working chamber changes with the movement of the piston 41; the piston 41 can enlarge and compress the working chamber when it moves back and forth in the piston chamber 32.

[0067] When the air pressure in the working chamber increases, the air relief valve plate is opened to release the compressed refrigerant in the working chamber from the working chamber. After the release, the air relief valve plate covers the end of the piston chamber 32. It should be noted that the air relief component is a relatively mature technology, and its specific structure will not be elaborated here.

[0068] like Figure 1-6 As shown, the driving unit includes a stator assembly 6 and a mover assembly 5. The mover assembly 5 cooperates with the stator assembly 6 and ultimately drives the piston 41 to move. The mover assembly 5 can move along the axial direction of the piston 41 relative to the stator assembly 6. During the movement, the mover assembly 5 drives the piston 41 to move in the piston cylinder 3.

[0069] In order to conveniently realize the movement control of the piston 3, the piston assembly 4 also includes a piston bracket 42, the piston 41 is mounted and fixed on the piston bracket 42, and the piston bracket 42 is located on the side of the piston 3 away from the piston cavity 32. The mover assembly 5 cooperates with the piston bracket 42, and the mover assembly 5 drives the piston bracket 42 to move in the axial direction parallel to the piston 41 during the movement process, and the piston bracket 42 drives the movement of the piston 41 during the movement process.

[0070] like Figure 3 As shown, the mover assembly 5 includes a mover frame 51 and a mover through hole 50 disposed on the mover frame 51. The mover frame 51 is disposed beside the piston cylinder 3. The piston bracket 42 is penetrated by the mover through hole 50 and is mounted and fixed on the mover frame 51. The mover assembly 5 also includes a driving magnet 52 disposed on the mover frame 51. The driving magnet 52 is disposed around the mover frame 51 to form a driving magnet ring.

[0071] The stator assembly 6 includes a stator frame 61 and a driving coil arranged on the stator frame 61, and the stator frame 61 is fixed on the frame 2; the driving coil is opposite to the driving magnet 52 and is arranged around the driving magnet 52 to form a driving coil ring, and the driving coil ring is coaxially arranged with the driving magnet ring; the electromagnetic force generated by the driving coil after being energized drives the driving magnet to reciprocate along the axial direction parallel to the piston 41.

[0072] In the prior art, the piston bracket 42 is generally installed and fixed on the inner wall of the mover through hole 50, a first installation portion is provided on the outer wall of the piston bracket 42, and a second installation portion is provided on the inner wall of the mover through hole 50, and the installation and fixation of the piston bracket 42 is completed by the cooperation of the first installation portion and the second installation portion. In the prior art, the aperture of the mover through hole 50 not only needs to include the outer diameter of the piston bracket 42 but also the size of the second installation portion, which means that the aperture of the mover through hole 50 needs to be larger than the outer diameter of the piston bracket 42, which results in the piston bracket 42 not being able to better match the mover through hole 50, and the space is wasted.

[0073] In order to avoid the above-mentioned problems, in the present embodiment, the piston bracket 42 is configured to penetrate the mover through hole and be fixedly installed on the end of the mover frame 51. Such a structural setting makes it possible for the mounting portion on the piston bracket 42 not to occupy the internal space of the mover through hole 50, thereby enabling the aperture of the entire mover through hole 50 to be shortened, thereby better achieving matching and fitting with the piston bracket 42, and making the structure of the entire compressor more compact.

[0074] like Figure 3 As shown, in a specific embodiment, the mover frame 51 includes an inner guard iron 511 and a pair of annular mounting members 512 disposed on opposite sides of the inner guard iron 511, and the piston bracket 42 is threadedly connected to an annular mounting member 512. The driving magnet 52 is disposed on the outer wall of the inner guard iron 511 and arranged along the circumferential direction of the inner guard iron 511.

[0075] like Figure 3-6 As shown, the outer part of the inner guard iron 511 is generally columnar and extends in parallel to the sliding direction of the piston 41. The mover through hole 50 is arranged at the center of the inner guard iron 511 and penetrates the inner guard iron 511 in the axial direction of the inner guard iron 511. After the piston assembly 4 is installed and fixed, part of the piston bracket 42 is penetrated by the mover through hole 50; the cross section of the inner guard iron 511 is generally annular.

[0076] A pair of annular mounting members 512 are arranged along the axial direction of the inner guard iron 511 and are respectively provided at both ends of the inner guard iron 511. The pair of annular mounting members 512 are respectively a first annular mounting member 5121 and a second annular mounting member 5122 arranged along the axial direction of the piston, wherein the first annular mounting member 5121 is located at a side farther from the piston cylinder 3 than the second annular mounting member 5122; the piston bracket 42 is threadedly connected to the first annular mounting member 5121.

[0077] like Figure 3-4As shown, the piston support 42 includes a support body 421 and an external threaded connection portion 422 disposed on the outer wall of the support body 421, and the mover frame 51 also has an internal threaded connection portion 514 disposed on the inner wall of the annular mounting member 512, and the internal threaded connection portion 514 is threadedly matched with the external threaded connection portion 422. The internal threaded connection portion 422 does not protrude from the inner wall of the mover through hole 50. The internal threaded connection portion 422 does not protrude from the inner wall of the mover through hole 50, which can better match the mover through hole 50 with the piston support 42.

[0078] Furthermore, the outer diameter of the piston bracket 42 increases as it moves away from the piston cylinder 3. The above-mentioned structure means that the outer diameter of the piston bracket 42 gradually decreases as it approaches the piston cylinder 3. The outer diameter of the piston bracket 42 gradually decreases from the external threaded connection portion 422 toward the piston cylinder 3, so that there is a larger gap between the piston bracket 42 that penetrates into the mover through hole 50 and the mover through hole 50, which facilitates the assembly of the piston 42.

[0079] In this embodiment, Figure 3-4 As shown, after the driving magnet 52 is installed and fixed to the inner guard iron 51, the outer surface of the driving magnet 52 can be basically flush with the outer surface of the inner guard iron 511. At this time, the driving magnet 52 is embedded in the inner guard iron 511. In this way, during the operation of the linear compressor, the magnetic field from the driving coil can better act on the driving magnet 52.

[0080] In order to achieve the flushing of the outer surface of the driving magnet 52 with the outer surface of the inner guard iron 511, a circle of inner guard iron avoidance grooves 5111 are formed on the outer wall of the inner guard iron 511. The inner guard iron avoidance grooves 5111 are arranged on the inner guard iron 511 and are formed concavely toward the mover through hole 50. The inner guard iron avoidance grooves 5111 are adapted to the driving magnet 52 and are used to position the driving magnet 52. Of course, in other embodiments, the driving magnet 52 can also be attached to the outer surface of the inner guard iron 511, and the driving magnet 52 protrudes from the outer wall of the inner guard iron 511 along the radial direction of the inner guard iron.

[0081] Due to the setting of the inner guard iron avoidance groove 5111, the part of the inner guard iron 511 where the driving magnet 52 is set is recessed into the rotor through hole 50, and an inner guard iron protrusion 5112 protruding toward the rotor through hole 50 is correspondingly formed on the inner wall of the rotor through hole 50 opposite to the position of the inner guard iron avoidance groove 5111; the internal threaded connection part 514 does not protrude from the inner guard iron protrusion 5112.

[0082] The inner guard iron 511 may be composed of a plurality of (e.g., ferromagnetic) laminations or have a plurality of laminations. The plurality of laminations are arranged around the circumferential direction of the inner guard iron 511 and are mounted or fixed together. After the plurality of laminations are arranged along the circumferential direction of the inner guard iron 511, the laminations may be connected and fixed to each other through the annular mounting member 512. Of course, the plurality of laminations may also be installed and fixed through other fixing rings to form the inner guard iron 511, and finally the inner guard iron 511 is connected and fixed to the annular mounting member 512.

[0083] Since the inner guard iron 511 is formed by stacking multiple layers of laminations, in order to facilitate the connection and fixation between the laminations, two annular mounting members 512 are provided. The two annular mounting members 512 are relatively arranged at the two ends of the inner guard iron 511. The two annular mounting members 512 connect and fix the several laminations constituting the inner guard iron 511 together.

[0084] like Figure 1-6 As shown, in this embodiment, the stator assembly 6 includes a stator frame 61 and a driving coil (not shown), the stator frame 61 includes an outer guard iron, the driving coil is arranged on the outer guard iron, the outer guard iron is integrally sleeved on the outside of the mover assembly 5, the stator frame 61 is integrally wound around the inner guard iron 51 in an annular shape and coaxially arranged with the inner guard iron 51, and a gap is left between the outer wall of the inner guard iron 511 and the stator frame 61. That is, in the radial direction of the inner guard iron 511, a gap is left between the outer guard iron and the inner guard iron 511, so that the inner guard iron 511 will not be disturbed by the outer guard iron when it moves in the axial direction.

[0085] In a specific embodiment, the outer guard iron and / or the driving coil may be extended around the inner guard iron 511. For example, the driving coil is formed and arranged around the circumference of the inner guard iron 511. The driving coil is opposite to the driving magnet 52. On the outer surface of the inner guard iron 511, the driving magnet 52 may face and / or be directly exposed to the driving coil; in the radial direction of the inner guard iron 511, a gap is left between the driving magnet 52 and the driving coil.

[0086] The driving coil is used to move the inner guard iron 511 in the axial direction. For example, a current can be induced in the driving coil to generate a magnetic field that engages with the driving magnet through a current source (not shown) and pushes the driving magnet 52 to move. The driving magnet 52 drives the inner guard iron 511 to move, and the inner guard iron 511 in turn drives the piston assembly 4 to move. The piston 41 compresses the refrigerant in the piston cylinder during the axial movement.

[0087] The linear compressor may include various components for allowing and / or regulating the operation of the linear compressor, such as a control unit (not shown), which is in communication connection or direct electrical connection with the drive coil. Therefore, the control unit can selectively activate the drive coil, thereby generating an induced current in the drive coil.

[0088] In a specific embodiment, Figure 3-6 As shown, in order to better realize the installation and fixation of the mover frame 61, the frame 2 includes a pair of annular fixing frames 21 and a locking member 22, and the locking member 22 clamps the stator frame 61 between the pair of annular fixing frames 21; the linear compressor also has elastic support legs 11, and the annular fixing frames 21 are fixed to the outer shell 1 through the elastic support legs 11; each annular fixing frame 21 is installed and fixed to the outer shell 1 through two elastic support legs 11.

[0089] The locking member 22 includes a locking screw 221, a limiting nut disposed on the locking screw 221, and a locking nut 222 matched with the locking screw 221. One end of the locking screw 221 away from the limiting nut is sequentially penetrated by two annular fixing frames 21 and is threadedly connected with the locking nut 222. The stator frame 61 is clamped and fixed between the two annular fixing frames 21. The cylinder body 31 of the piston cylinder 3 is mounted and fixed on the annular fixing frame 21.

[0090] It can be understood that, in order to better achieve the installation and fixation of the ring fixing frame 21, a plurality of locking members 22 can be provided. In the present embodiment, four locking members 22 are provided, and the four locking members 22 are arranged in a ring shape.

[0091] The mover assembly 5 can move along the axial direction of the piston 41 . The mover assembly 5 needs to be supported in the radial direction. In addition, the mover assembly 5 also needs to move relative to the stator assembly 6 in the axial direction of the piston 41 .

[0092] In order to realize the above-mentioned setting of the moving subassembly 5, as Figure 5-6 As shown, in this embodiment, the linear compressor also has a connecting component 8, which includes a plurality of elastic members 81. The elastic member 81 has a fixed end 811 and a free end 812 that are relatively arranged. The fixed end 811 is fixed on the frame 2; the free end 812 is connected and fixed to the inner guard iron 511, and the elastic member 81 can be elastically deformed to allow the free end 812 to move relative to the fixed end 811.

[0093] The setting of the elastic member 81 not only realizes the fixed support of the movable assembly 5, but also can enhance the axial movement of the movable assembly 5 in the piston 41. After deformation, the elastic member 81 accumulates rebound force and the rebound force and the magnetic force generated by electromagnetic induction act on the movable assembly 5 to make the movable assembly 5 move relative to the stator assembly 6.

[0094] In order to better prevent the elastic member 81 from restricting the movement of the mover assembly 5 , the elastic member 81 is curved as a whole, and the curvature of the elastic member 81 is consistent with the curvature of the cross-sectional circle of the inner guard iron 511 .

[0095] like Figure 7-13As shown, in a specific embodiment, the piston bracket 42 includes a bracket body 421 and a ball head structure 424 arranged on the bracket body 421, and a hemispherical recess 414 adapted to the ball head structure 424 is formed on the side of the piston 41 away from the piston cavity 32, and the ball head structure 424 can move in the hemispherical recess 414.

[0096] The piston 41 and the bracket body 421 are combined through the cooperation of the ball head structure 424 and the hemispherical recess 414, which can realize relative rotation between the piston 41 and the bracket body 421. Compared with the piston 41 being completely fixed on the bracket body 421, the solution of this embodiment can better control the movement of the piston 41, and the piston 41 has greater flexibility during the movement, which can reduce the wear of the piston 41.

[0097] In the prior art, the piston 41 is driven by the piston bracket 42. Since the piston bracket 42 is in the shape of a long axis as a whole, it is difficult to completely control the movement of the piston bracket 42 along the axial direction of the piston 41. That is, the piston bracket 42 will more or less deviate from the axial direction of the piston 41 during the movement, or if the cylinder body 31 of the piston cylinder 3 is not accurate enough, the piston 41 is prone to greater wear when moving in the piston cylinder 3.

[0098] The present invention provides a ball head structure so that the piston 41 and the piston bracket 42 can move slightly relative to each other in the radial direction while moving along the axial direction of the piston 41, thereby reducing the deviation of the sliding direction of the piston 41 caused by the deviation of the piston bracket 42 during movement, and reducing the wear of the piston 41.

[0099] In addition, since the piston bracket 42 and the piston 41 can move relative to each other, it is more convenient to assemble the piston assembly 4 onto the mover assembly 5 .

[0100] It should be noted that the hemispherical depression 414 is not necessarily limited to a hemispherical shape. What is intended here is that the hemispherical depression 414 forms a certain fit with the ball head structure 424 so that the two can move relative to each other. The hemispherical depression 414 can be a curved surface, and the ball head structure 424 can also be a curved surface of other shapes instead of a hemispherical shape.

[0101] As a preferred solution, the hemispherical recess 414 and the ball head structure 424 are completely matched in shape, so that the two can better cooperate and move, but this requires too high precision in the production process. When the production precision is not required enough, the ball head is prone to wear.

[0102] In order to better use the curvature of the curved surface of the hemispherical recess 414 is not greater than the curvature of the curved surface of the ball head structure 424. When the hemispherical recess 414 and the ball head structure 424 are both hemispherical, the shape of the hemispherical recess 414 is larger and can wrap the ball head structure 424, that is, the radius of the circle where the curved surface of the hemispherical recess 414 is located is greater than the radius of the circle where the curved surface of the ball head structure 424 is located. In this case, it can be seen that the small spherical ball head structure 424 moves in the large spherical recess.

[0103] In this embodiment, if Figure 8 As shown, the ball head structure 424 is pressed and fixed on the bracket body 421 under the action of the piston 41 , and the ball head structure 424 is pressed and fixed on the end of the bracket body 421 .

[0104] Specifically, the piston assembly 4 also has a fastening structure 44; the fastening structure 44 includes a fastening support plate 441 fixed on the bracket body 421 and a fastener 442 arranged on the fastening support plate 441, and the fastener 442 is fixed on the piston 41 away from the side of the fastening support plate 441.

[0105] Under the action of the fastener 442 , the ball head structure 424 is pressed and positioned at the end of the bracket body 421 .

[0106] like Figure 8 and Fig.13 As shown, the fastener 442 is a bolt body, and the piston 42 is provided with a fastener connecting column 415 that is threadedly matched with the fastener 442, and the fastener connecting column 415 is arranged at the bottom of the hemispherical recess 414 and located at the center of the hemispherical recess 414;

[0107] The fastening support plate 441 is provided with a through hole adapted to the bolt body, and a bolt cap is provided on the end of the bolt body away from the piston 41; the fastening structure 44 also has a compression spring 443 sleeved outside the bolt body and respectively abutting against the bolt cap and the fastening support plate. The provision of the compression spring 443 enables the fastening structure 44 to more flexibly press the ball head structure 424 onto the bracket body 421.

[0108] In the above structure, since the ball head structure 424 is pressed against the end of the bracket body 421, and the end of the bracket body 421 is generally annular, the contact area between the ball head structure 424 and the bracket body 421 is limited. Such a structural setting will increase the wear of the ball head structure 424 during the activity, thereby weakening the strength of the ball head structure 424.

[0109] In order to avoid the above problems, Figure 8-14As shown, the piston bracket 42 further includes a ball head support member 425 , which is positioned and supported on the bracket body 421 , and at least a portion of the ball head structure 424 is sleeved outside the ball head support member 425 .

[0110] The setting of the ball head support 425 plays a role in supporting the ball head structure 424. After installation and fixation, the end of the ball head structure 424 not only abuts against the direct body 421, but can also be wrapped and fit on the ball head support 425. Through contact at multiple positions, the ball head structure 424 can achieve more stable fixed support, thereby improving the stability of installation and fixation.

[0111] In this embodiment, if Figure 8 As shown, the bracket body 421 has a bracket cavity 420 , and a positioning piece 4212 is provided on the inner wall of the bracket cavity 420 . The ball head support piece 425 is inserted into the bracket cavity 420 from the end of the bracket body 421 and pressed against the positioning piece 4212 .

[0112] After installation and fixation, the ball head structure 424 partially contacts the ball head support 425, and the end of the ball head structure 424 is pressed against the end of the support body 423. The above-mentioned structural arrangement provides the ball head structure 424 with more supporting positions, thereby achieving more stable installation and fixation.

[0113] Specifically, Fig.14 As shown, the ball head support member 425 has an annular positioning portion 4251 positioned on the bracket body 421 and a ball head coupling ring 4252 coaxially arranged with the annular positioning portion 4251;

[0114] A bracket positioning groove 4211 matched with the annular positioning portion 4251 is formed on the bracket body 421, and the positioning piece forms the bottom of the bracket positioning groove 4211. After the ball head support 425 is installed and fixed, the annular positioning portion 4251 penetrates into the bracket positioning groove 4211, and the end of the annular positioning portion 4251 is tightly pressed against the positioning piece.

[0115] The ball head structure 424 is provided with a ball head positioning hole 4241 , and the ball head coupling ring 4252 is positioned in the ball head positioning hole 4241 and supports the ball head structure 424 .

[0116] In this embodiment, the outer diameter of the ball head coupling ring 4252 is smaller than the outer diameter of the annular positioning portion 4251 , and the outer diameter of the ball head coupling ring 4252 gradually decreases as it moves away from the annular positioning portion 4251 .

[0117] During use, the refrigerant enters the piston cavity 32 through the piston air inlet passage on the piston 41. In order to better realize the transmission of the refrigerant, the piston assembly 4 also includes a support cavity 420 connected to the piston air inlet passage. In this embodiment, the support cavity 420 is arranged on the piston support 42. In other embodiments, when there is no piston support 42, the support cavity 420 can also exist in other structures as carriers. The support cavity 420 only serves as a flow channel for the refrigerant to be transmitted to the piston air inlet passage.

[0118] After the refrigerant is sucked into the flow channel, the piston valve plate 43 opens to connect the piston air inlet channel and the piston chamber, so that the refrigerant is sucked into the piston chamber for piston compression. After the refrigerant enters, the piston valve plate 43 closes to close the connection between the piston air inlet channel and the piston chamber.

[0119] In the prior art, in order to ensure sufficient air intake, the air intake channel generally includes multiple air intake holes. The provision of multiple air intake holes requires the piston valve plate 43 to cover multiple air intake holes at the same time, which puts certain requirements on the size of the piston valve plate 43. The increase in the size of the piston valve plate 43 will inevitably increase the difficulty of opening the piston valve plate 43.

[0120] In order to better realize the opening of the piston valve plate 43, as Figure 8-13 As shown, in this embodiment, the piston intake channel includes a converging groove 411 arranged on the piston 41 and a plurality of intake holes 412 connected to the converging groove 411, the converging groove 411 is arranged on the side of the piston 41 facing the piston cavity 32, and the piston valve plate 43 includes a valve plate body 431 adapted to the opening of the converging groove 411.

[0121] In this embodiment, different air inlet holes 412 are converged by setting a convergence groove 411, and the piston valve plate 43 can be designed accordingly by designing the opening shape of the convergence groove 411, thereby getting rid of the problem that the structure of the piston valve plate 43 is limited by the number and distribution of the air inlet holes 412, and the piston valve plate 43 can be better designed to achieve better opening of the piston valve plate 43.

[0122] In a specific embodiment, Figure 12-13 As shown, the air inlet 412 includes a first hole body 4121 located at the bottom of the converging groove 411 and a second hole body 4122 located at the side wall of the converging groove 411. In this embodiment, the air inlet 412 is arranged at the bottom and the side wall of the converging groove 411 at the same time, so that the air inlet 412 has a larger flow area, and the flow rate of the refrigerant can be not affected when the piston valve plate 43 is designed. The design of the converging groove 411 in this embodiment is actually to convert the circular air inlet into an annular air outlet. Compared with the circular air inlet, the annular air outlet can be more conveniently controlled.

[0123] In this embodiment, if Fig.12 As shown, there are multiple air inlet holes 412, and the multiple air inlet holes 412 are arranged in an annular shape. The convergence groove 411 is also arranged in an annular shape as a whole. A valve plate mounting column 413 is arranged at the center of the piston 41, and the convergence groove 411 is arranged around the valve plate mounting column 413; the outer wall of the valve plate mounting column 413 forms the inner wall of the convergence groove 411; the valve plate body 431 is also arranged in an annular shape and is adapted to the annular convergence groove 411. The valve plate body 431 covers the opening of the convergence groove 411 so that the piston flow channel and the piston cavity 32 are closed. When the valve plate body 431 leaves the opening of the convergence groove 411, the piston flow channel and the piston cavity 32 are opened.

[0124] It is understandable that the piston valve plate 43 also has a mounting plate 432 fixed to the valve plate mounting column 413 and a connecting plate 433 connected to the mounting plate 432 and the valve plate body 431 . The connecting plate 433 can be elastically deformed to drive the valve plate body 431 to detach from covering the convergence groove 411 .

[0125] When the gas pressure of the refrigerant in the piston flow channel increases, the valve plate body 431 is pushed to move away from the convergence groove 411 to open the convergence groove 411. At this time, the connecting plate 433 produces elastic deformation, and the connecting plate 433 continues to have a rebound force to drive the valve plate body 431 to return to its original position and rebound after the gas pressure in the piston flow channel decreases, thereby achieving the closure of the convergence groove 411.

[0126] In actual use, the size of the connecting piece 433 and the size of the valve body 431 affect each other. When the size of the valve body 431 is too large, the size of the connecting piece 433 will be reduced accordingly, which will increase the difficulty of opening the piston valve 43. It should be noted that the size here mainly refers to the length that the connecting piece 433 can extend between the valve body 431 and the mounting piece 432. When the size of the valve body 431 is too small, the size of the connecting piece 433 can be increased accordingly, so as to more conveniently realize the elastic deformation of the connecting piece 433, thereby making it easier to open the connecting piece 433.

[0127] In this embodiment, different air inlet holes 412 are gathered together by setting a converging groove 411, so that the valve plate body 431 that originally covers multiple air inlet holes 412 at the same time is transformed into only needing to cover the converging groove 411, which facilitates the control of the piston flow channel and can also better realize the setting of the valve plate body 431, so that the valve plate body 431 has a narrower width, thereby realizing convenient control of the opening of the piston valve plate 43.

[0128] like Fig. 9As shown, a plurality of connecting pieces 433 may be provided, and the plurality of connecting pieces 433 are arranged in a ring shape with the mounting piece 432 as the center. In the present embodiment, two connecting pieces 433 are provided, and the two connecting pieces 433 are symmetrically arranged with the mounting piece 432 as the symmetry point. In the present embodiment, since the valve piece body 431 is adapted to the structure of the convergence groove and is also arranged in a ring shape as a whole, and the mounting piece 432 is also circular as a whole, the overall shape of the piston valve piece 43 is a central symmetrical pattern. Such a structural setting can conveniently realize the installation and fixation of the piston valve piece 43, and the piston valve piece 43 will not be excessively restricted during the installation and fixation process.

[0129] Furthermore, in order to better control the piston flow channel, the convergence groove 411 is configured such that the opening of the convergence groove 411 gradually narrows as it moves away from the bottom of the convergence groove 411. The gradually narrowing opening of the convergence groove 411 can achieve better control of the opening of the convergence groove 411.

[0130] The refrigerant will generate a lot of noise during the flow process. In order to reduce the noise, Figure 8-17 As shown, the linear compressor further includes a silencer structure 7. In this embodiment, the silencer structure 7 is disposed in the support cavity 420, that is, silencer is completed before the refrigerant enters the flow channel.

[0131] Specifically, Figure 15-17 As shown, the muffler structure 7 includes a muffler pipe 71 having a flow channel 70, the flow channel 70 is connected to the support cavity 420, the flow channel 70 has a flow inlet 701 and a flow outlet 702, and the flow outlet 702 of the flow channel is directly exposed to the support cavity 420. The muffler pipe 71 includes a tube body 711, and the muffler structure 7 also includes a plurality of partition plates 72 arranged on the outer wall of the tube body 711, the plurality of partition plates are arranged along the axial direction of the tube body 711, the partition plates 72 are attached to the inner wall of the support cavity 420, and a muffler cavity 73 is formed between two adjacent partition plates 72, and a tube body through hole 712 connecting the flow channel 70 and the muffler cavity 73 is provided on the tube body 711.

[0132] Each of the muffler chambers 73 is provided with a plurality of tube body through holes 712, which are arranged along the circumferential direction of the tube body 711. In this embodiment, one muffler chamber 73 is provided with two tube body through holes 712, which are arranged on opposite sides of the tube body 711.

[0133] It should be noted that each partition plate 72 is extended along the circumferential direction of the tube body 711, and the partition plate 72 is integrally sleeved outside the tube body 711, and a silencer cavity 73 is formed between two adjacent partition plates 72, part of the outer wall of the tube body 711 and part of the inner wall of the bracket cavity 420.

[0134] In this embodiment, a plurality of silencer cavities 73 are provided, and the plurality of silencer cavities 73 are arranged along the axial direction of the tube body 711. Different silencer cavities 73 have different sizes, and different silencer cavities 73 are used to eliminate different noises, thereby achieving a better noise reduction effect.

[0135] During the flow process, the refrigerant mainly flows along the axial direction of the tube body 711, and flows in the tube cavity of the tube body 711. The tube cavity serves as a part of the flow channel 70. During the flow process, the refrigerant will enter different silencer chambers 73 through the tube body through hole 712. The existence of the silencer chamber 73 has a certain buffering effect on the flowing refrigerant, thereby achieving a noise reduction effect.

[0136] In this embodiment, the opening shape of the tube body through hole 712 is generally strip-shaped, and the opening of the tube body through hole 712 is generally extended along a first direction, and the first direction is parallel to the axial direction of the tube body 711, that is, the opening shape of the tube body through hole 712 is generally extended in a direction parallel to the axial direction of the tube body 711.

[0137] The opening shape of the tube body through hole 712 is actually parallel to the flow direction of the refrigerant. The purpose of this design is to enable the refrigerant to enter the silencer chamber 73 more smoothly, so that the silencer chamber 73 can have a better silencer effect, and after the refrigerant enters the silencer chamber 73, it is easy to form a vortex, and the formed vortex can further enhance the silencer effect.

[0138] In this embodiment, the opening shape of the tube body through hole 712 is generally rectangular and has a length direction and a width direction. The length direction of the opening shape of the tube body through hole 712 is parallel to the axial direction of the tube body 711 .

[0139] In this embodiment, as the outer diameter of the piston bracket 42 gradually increases away from the piston 41, the size of the bracket cavity 420 provided in the piston bracket 42 also gradually increases, and the distance between two adjacent partition plates 72 also gradually increases away from the piston 41.

[0140] In one embodiment (not shown), the tube cavity is the flow channel 70, the flow inlet 701 and the flow outlet 702 are arranged on opposite sides of the tube body 711, and the opening direction of the flow outlet 702 is toward the axial direction of the tube body 711, that is, toward the piston 41, so that the refrigerant fluid coming out of the flow channel 70 directly rushes into the piston 41, which is not only easy to damage the piston valve plate 43 on the piston 41, but also generates a lot of noise.

[0141] Further, in order to avoid the above problems, in another embodiment, Figure 15-17As shown, the muffler structure 7 includes a muffler pipe 71 having a flow channel 70 . The muffler pipe 71 has a flow outlet 702 exposed toward the support cavity 420 near the piston 41 . The opening direction of the flow outlet 702 is oblique to the axial direction of the piston 41 .

[0142] Specifically, the opening direction of the flow outlet 702 of the circulation channel 70 is not along the axial direction of the piston 41, which can avoid affecting the piston valve plate 431 on the piston 41. At the same time, since the entire flow channel of the refrigerant has added a certain degree of bending, the flow velocity can be buffered and the large noise generated by the refrigerant during the transmission process can be effectively reduced.

[0143] In a specific embodiment, the opening direction of the flow outlet 702 is perpendicular to the axial direction of the piston 41, that is, the opening direction of the flow outlet 702 is along the radial direction of the tube body 711. A plurality of flow outlets 702 are provided, and the plurality of flow outlets 702 are arranged along the circumferential direction of the muffler 71.

[0144] In order to realize the above-mentioned setting of the flow outlet 702, the muffler pipe 71 includes a pipe body 711 having a pipe cavity, a baffle 74 and a baffle support column 75;

[0145] The tube body 711 extends along an axial direction parallel to the piston 41 and has a proximal end and a distal end that are relatively arranged. The proximal end of the tube body 711 is closer to the piston 41 than the distal end; the baffle 74 is fixed to the proximal end of the tube body 711 by a baffle support column 75 and the baffle 74 is opposite to the tube cavity; the flow outlet 702 of the flow channel 70 is arranged between the baffle 74 and the proximal end of the tube body 711.

[0146] The blocking piece 74 actually blocks the outlet of the lumen, thereby preventing the outlet of the lumen from directly facing the piston 41 .

[0147] In a specific embodiment, two baffle support columns 75 are provided, and two flow outlets 702 disposed opposite to each other are formed between the two baffle support columns 75 .

[0148] The flow outlet 702 can be regarded as a lateral opening formed on the side wall of the tube body 711 . The proximal end of the tube body 711 is blocked, and an opening in a radial direction is formed on the side wall of the tube body 711 .

[0149] When the flow outlet 702 is opened along the radial direction of the tube body 711, the position of the flow outlet 702 and the position of the tube body through hole 712 are staggered in the axial direction of the tube body 711, that is, the flow outlet 702 and the tube body through hole 712 are not opposite to each other in the axial direction of the tube body 711, and the two are not in a straight line. Such a structural setting can better increase the strength of the tube body 711.

[0150] The refrigerant will enter the buffer chamber 4201 after the flow outlet 702 of the flow channel 70. The buffer chamber 4201 is a part of the support chamber 420 and is surrounded by the support chamber 420, the partition plate 72 and the piston 41. The position where the partition plate 72 is arranged in the support chamber 420 forms an installation chamber opposite to the buffer chamber 4201. The muffler chamber 73 is actually a part of the installation chamber. The partition plate 72 and the tube body 711 divide the installation chamber into different chambers to form the muffler chamber 73.

[0151] After entering the buffer chamber, the refrigerant continuously increases the gas pressure in the buffer chamber. When the gas pressure reaches a certain height, the piston valve plate 43 is opened, so that the refrigerant in the buffer chamber flows into the piston chamber 32 .

[0152] In the prior art, the partition plate 72 is generally arranged on the entire tube body 711 along the axial direction of the tube body 711. Such a structural setting compresses the volume of the buffer chamber 4201, so that a large amount of refrigerant cannot be stored in the buffer chamber 4201, which makes it difficult to open the piston valve plate 43 in the subsequent process of opening the piston valve plate 43.

[0153] In order to avoid the above problem, in a specific embodiment, the partition plate 72 is disposed as a whole on the tube body 711 at a position relatively far away from the piston 41 .

[0154] The tube body 711 extends along the axial direction parallel to the piston 41 and has a proximal end and a distal end that are relatively arranged. The proximal end is located closer to the piston 41 relative to the distal end, and the flow outlet 702 is arranged at the proximal end of the tube body 711; the partition plate 72 is arranged as a whole on the tube body and is relatively close to the distal end.

[0155] The tube body 711 comprises a mounting section 7111 and an extension section 7112 which are arranged in parallel along the axial direction of the piston. The extension section 7112 is extended from the end of the mounting section 7111 toward the piston 41. The partition plate 72 is arranged on the mounting section 7111.

[0156] A buffer chamber 4201 is formed between the outer wall of the extension section 7112 , the piston 41 , the partition plate 72 and a portion of the inner wall of the bracket cavity 420 . The buffer chamber 4201 is connected to the flow channel 70 , and the flow outlet 701 is exposed toward the buffer chamber 4201 .

[0157] The piston valve plate 43 is arranged on the side of the piston 41 away from the buffer chamber 4201, that is, on the side of the piston 41 away from the muffler structure 7. After the refrigerant passes through the flow channel 70, it enters the buffer chamber 4201, and the air pressure in the buffer chamber 4201 increases. After the air pressure increases, the piston valve plate 43 is lifted, thereby opening the piston air inlet channel.

[0158] In the prior art, since the volume of the buffer chamber 4201 is relatively large, the refrigerant stored in the buffer chamber 4201 is relatively small, and it is difficult to push the piston valve plate 43 to open. In order to avoid the above problems, the piston valve plate 43 is generally made very thin. Such a structural setting can easily cause damage to the piston valve plate 43, thereby causing the piston valve plate 43 to fail. In this embodiment, the space in the buffer chamber 4201 is increased by changing the distribution of the partition plate 72 on the muffler 71. The increased space in the buffer chamber 4201 can accumulate more refrigerant in the buffer chamber 4201, thereby forming a greater force to push the piston valve plate 43 to open, and conveniently realize the setting of the piston valve plate 43. At the same time, the thickness of the piston valve plate 43 can also be increased to improve the stability of the piston valve plate 43 during operation.

[0159] The compressor further includes an oil pumping system 9 , which provides lubricating oil to the piston chamber 32 .

[0160] The oil pumping system 9 includes an oil pump 91, an oil inlet channel 90 and an oil suction pipe 92. The oil pump 91 has an oil inlet and an oil outlet that are relatively arranged. The oil inlet channel 90 connects the oil outlet of the oil pump 91 with the piston chamber 32; the oil suction pipe 92 is arranged at the oil inlet of the oil pump 91, and the oil suction pipe 92 extends toward the bottom of the accommodating chamber 10, and the inlet of the oil suction pipe 92 is relatively located close to the center of the outer shell 1.

[0161] The center position of the shell 1 is the lowest position of the accommodating chamber 10, so the lubricating oil will gather here after being sprayed into the accommodating chamber 10. By setting the oil suction pipe 92 and setting the inlet of the oil suction pipe 92 near the center position of the shell 1, it is easier to absorb the lubricating oil and improve the oil intake efficiency.

[0162] The cross section of the housing 1 along the horizontal direction has a length direction and a width direction, and the inlet of the oil suction pipe 92 is relatively located at the center position of the housing 1 in the width direction.

[0163] The oil pump 91 includes an oil pump housing 911 and an oil pump piston 912 disposed in the oil pump housing 911; the oil pump piston 912 slides along the axial direction of the oil pump housing 911, and the oil pump 91 also includes an oil outlet pipe 913, which serves as a part of the oil inlet passage 90;

[0164] The oil outlet pipe 913 and the oil suction pipe 92 are located on opposite sides of the oil pump housing 911 in the axial direction.

[0165] The oil pump piston 912 moves in the oil pump housing 911 and divides the space in the oil pump housing 911 into a first chamber and a second chamber. The oil pump 91 also includes a pair of springs arranged on opposite sides of the oil pump piston 912, and the pair of springs are respectively arranged in the first chamber and the second chamber. The oil pump piston 912 also has a connecting hole connecting the first chamber and the second chamber.

[0166] The compressor also has a mixed liquid disposed in the housing 1, the mixed liquid including a mixed liquid of lubricating oil and refrigerant, and the mixed liquid is disposed in the accommodating chamber 10. The oil pump 91 is located above the liquid level of the mixed liquid, the oil suction pipe 92 is disposed at the oil inlet of the oil pump 91, and one end of the oil suction pipe 92 away from the oil pump 91 extends below the liquid level of the mixed liquid.

[0167] In the prior art, in order to facilitate the absorption of the mixed liquid, the oil pump 91 is generally immersed in the mixed liquid. The oil pump 91 will vibrate during use, and when the oil pump 91 is immersed in the mixed liquid, its vibration process will generate a large noise. In this embodiment, the oil pump 91 is arranged on the surface of the mixed liquid, and the mixed liquid is absorbed by the arrangement of the oil suction pipe 92, so that the noise generated during the use of the compressor can be effectively reduced.

[0168] Another embodiment of the present invention further discloses a refrigeration device, including a box and a refrigeration system arranged on the box, wherein the refrigeration system includes a linear compressor, a condenser, a throttling device and an evaporator connected in series in sequence. The linear compressor is the linear compressor described above. The refrigeration device of the embodiment of the present invention can be a refrigerator, a freezer or a wine cabinet, etc.

[0169] The above describes in detail the structure, features and effects of the present invention based on the embodiments shown in the drawings. The above is only a preferred embodiment of the present invention, but the present invention is not limited to the scope of implementation shown in the drawings. Any changes made according to the concept of the present invention, or modifications to equivalent embodiments with equivalent changes, which still do not exceed the spirit covered by the description and drawings, should be within the protection scope of the present invention.

Claims

1. A linear compressor, characterized in that: include: A housing, a frame arranged in the housing, a piston cylinder arranged on the frame, a piston assembly and a driving unit; The piston cylinder has a cylinder body and a piston cavity penetrating the cylinder body, the piston assembly includes a piston, and the driving unit drives the piston to reciprocate in the piston cavity; The piston is provided with a piston air inlet channel connected to the piston cavity, the piston assembly has a bracket cavity connected to the piston air inlet channel and a silencer structure provided in the bracket cavity, the silencer structure includes a silencer pipe with a flow channel, the silencer pipe has a flow outlet exposed toward the bracket cavity at a position close to the piston, and the opening direction of the flow outlet is oblique to the axial direction of the piston.

2. The linear compressor according to claim 1, characterized in that: An opening direction of the flow outlet is perpendicular to an axial direction of the piston.

3. The linear compressor according to claim 2, characterized in that: The flow outlets are provided in plurality, and the plurality of flow outlets are arranged along the circumferential direction of the muffler pipe.

4. The linear compressor according to claim 2, characterized in that: The muffler pipe comprises a pipe body with a pipe cavity, a baffle and a baffle support column; The tube body is extended in a direction parallel to the axial direction of the piston and has a proximal end and a distal end that are arranged opposite to each other, and the proximal end of the tube body is closer to the piston than the distal end; the baffle is fixed to the proximal end of the tube body by the baffle support and the baffle is opposite to the lumen; The flow outlet is arranged between the baffle and the tube body.

5. The linear compressor according to claim 4, characterized in that: There are two baffle support columns, and two flow outlets arranged opposite to each other are formed between the two baffle support columns.

6. The linear compressor according to claim 1, characterized in that: The silencer pipe includes a pipe body and a plurality of partition plates arranged on the outer wall of the pipe body, wherein the plurality of partition plates are arranged along the axial direction of the pipe body, the partition plates are attached to the inner wall of the piston support, and a silencer cavity is formed between two adjacent partition plates, and a pipe body through hole connecting the flow channel and the silencer cavity is arranged on the pipe body.

7. The linear compressor according to claim 6, characterized in that: As the distance from the piston increases, the outer diameter of the piston support gradually increases, and the outer diameter of the tube body also gradually increases.

8. The linear compressor according to claim 1, characterized in that: The linear compressor also has an air release assembly, which includes an air release valve plate disposed on one side of the cylinder body and used to open or close the piston chamber; a working chamber is formed between the piston and the air release valve plate, and the driving unit drives the piston to reciprocate in the piston chamber to expand or compress the working chamber; The piston assembly further comprises a piston valve plate, which moves on the piston to control the connection or closing of the piston air inlet passage and the working chamber.

9. The linear compressor according to claim 1, characterized in that: The driving unit comprises a stator assembly and a mover assembly, and the mover assembly drives the piston to move back and forth in the piston cylinder; The stator assembly is disposed on the frame and cooperates with the mover assembly to drive the mover assembly to move; The mover frame comprises an inner guard iron and a driving magnet arranged on the outer wall of the inner guard iron, wherein the driving magnet is arranged in an annular shape on the outer wall of the inner guard iron to form a driving magnet ring; The stator assembly includes a stator frame and a driving coil arranged on the stator frame, and the stator frame is fixed on the frame; the driving coil is opposite to the driving magnet and is arranged around the driving magnet to form a driving coil ring, and the driving coil ring is coaxially arranged with the driving magnet ring; the electromagnetic force generated by the driving coil after being energized drives the driving magnet to reciprocate along the axial direction of the piston.

10. A refrigeration device, characterized in that: It comprises a box body and a refrigeration system arranged on the box body, wherein the refrigeration system comprises the linear compressor according to any one of claims 1 to 9.

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