CN220955954U - Linear compressor and refrigeration equipment - Google Patents

Abstract

The utility model discloses a linear compressor and refrigeration equipment, wherein the linear compressor comprises: the device 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, and the piston assembly comprises a piston and a driving unit; the piston is provided with a piston air inlet channel, the piston assembly further comprises a support cavity and a silencing structure, the silencing structure comprises a silencing pipe with a flow channel, the flow channel is communicated with the support cavity, the silencing pipe comprises a pipe body and a plurality of partition plates, the partition plates are distributed along the axial direction of the pipe body, a silencing cavity is formed between every two adjacent partition plates, and a pipe body through hole for communicating the flow channel with the silencing cavity is formed in the pipe body; the whole opening of the tube body through hole is strip-shaped and extends towards the axial direction parallel to the tube body. The utility model can enable the refrigerant to smoothly enter the silencing cavity, thereby enabling the silencing cavity to have better silencing effect.

Description

Linear compressor and refrigeration equipment

Technical Field

The utility model relates to the technical field of linear compressors, in particular to a linear compressor and refrigeration equipment.

Background

A compressor is a mechanical device that compresses air, refrigerant, or other various working gases and increases the pressure thereof by receiving power from a power generating device such as a motor or a turbine. Compressors are widely used in home appliances such as refrigerators and air conditioners or in the entire industrial field.

The linear compressor is used as a compressor, and the control of the piston movement is realized through the linear reciprocating driving motor, compared with a non-linear compressor, the linear compressor does not need motion conversion, so that the mechanical loss caused by operation conversion is avoided, the compression efficiency can be improved, and the integral structure is simplified.

In the linear compressor, a piston linearly reciprocates in a piston cylinder to compress refrigerant introduced into a compression space; the refrigerant can produce great noise at the flow in-process, in order to reduce noise, linear compressor still includes amortization structure, and the design amortization effect of amortization structure is not showing enough among the prior art.

Disclosure of utility model

The utility model aims to provide a compressor, which solves the defects in the prior art and can enable a refrigerant to smoothly enter a silencing cavity, so that the silencing cavity has a better silencing effect.

The compressor provided by the utility model comprises: the device 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 also comprises a bracket cavity communicated with the piston air inlet channel and a silencing structure arranged in the bracket cavity,

The silencing structure comprises a silencing pipe with a flow channel, wherein the flow channel is communicated with the bracket cavity, the silencing pipe comprises a pipe body and a plurality of partition plates arranged on the outer wall of the pipe body, the partition plates are arranged along the axial direction of the pipe body, the partition plates are attached to the inner wall of the bracket cavity, a silencing cavity is formed between two adjacent partition plates, and a pipe body through hole for communicating the flow channel with the silencing cavity is formed in the pipe body; the whole opening of the tube body through hole is strip-shaped and extends towards the axial direction parallel to the tube body.

Further, the opening of the pipe body through hole is integrally formed and has a length direction and a width direction, and the length direction of the pipe body through hole is parallel to the axial direction of the pipe body.

Further, the pipe body through holes are arranged in a plurality of ways and are distributed along the circumferential direction of the pipe body.

Further, each silencing cavity is provided with a corresponding pipe body through hole communicated with the flow channel, and the pipe body through holes in different silencing cavities are distributed along the axial direction parallel to the pipe body.

Further, the outer diameter of the piston support gradually increases with distance from the piston, and the distance between two adjacent partition plates also gradually increases.

Further, the piston assembly further comprises a piston support, the piston support comprises a support body and a ball head structure arranged on the support body, the support cavity is arranged on the support body, a hemispherical recess matched with the ball head structure is formed on one side, away from the piston cavity, of the piston, and the ball head structure can move in the hemispherical recess;

The piston support further comprises a ball head support piece, the ball head support piece is positioned and supported on the support body, and at least part of the ball head structure is sleeved outside the ball head support piece.

Further, the linear compressor is further provided with a gas leakage assembly, and the gas leakage assembly comprises a gas leakage valve plate which is arranged on one side of the cylinder body and used for opening or closing the piston cavity; a working cavity is formed between the piston and the air leakage valve plate, and the driving unit drives the piston to reciprocate in the piston cavity so as to enlarge or compress the working cavity;

The piston assembly further comprises a piston valve plate which moves on the piston to control the connection or disconnection of the piston air inlet channel and the working cavity.

Further, the piston air inlet channel comprises a converging groove and a plurality of air inlet holes communicated with the converging groove, the converging groove is arranged on one side of the piston facing the working cavity, and the piston valve plate comprises a valve plate body matched with the opening of the converging groove.

Further, the driving unit comprises a stator assembly and a rotor assembly, the piston assembly further comprises a piston support, the piston is fixed on the piston support, and the rotor assembly drives the piston support to reciprocate along the axial direction of the piston;

The stator component is arranged on the frame body and matched with the rotor component to drive the rotor component to move;

the mover frame body comprises an inner back iron and a driving magnet arranged on the outer wall of the inner back iron, and the driving magnet is annularly arranged on the outer wall of the inner back iron to form a driving magnet ring;

The stator assembly comprises a stator frame body and a driving coil arranged on the stator frame body, and the stator frame body is fixed on the frame body; the driving coil is opposite to the driving magnet in position and surrounds the driving magnet to form a driving coil ring, and the driving coil ring and the driving magnet ring are coaxially arranged; the electromagnetic force generated after the driving coil is electrified drives the driving magnet to reciprocate along the axial direction of the piston.

The utility model also discloses refrigeration equipment, which comprises a box body and a refrigeration system arranged on the box body, wherein the refrigeration system comprises the linear compressor.

Compared with the prior art, the silencing structure of the linear compressor has the advantages that the opening shape of the through hole of the pipe body is parallel to the flowing direction of the refrigerant, so that the refrigerant can smoothly enter the silencing cavity, the silencing cavity has a better silencing effect, vortex is easy to form after the refrigerant enters the silencing cavity, and the formed vortex can further enhance the silencing effect.

Drawings

FIG. 1 is a schematic view showing an installation structure of a linear compressor in a housing according to an embodiment of the present utility model;

FIG. 2 is a top view of FIG. 1;

FIG. 3 is a cross-sectional view taken along the direction AA in FIG. 2;

FIG. 4 is a partial enlarged view at B in FIG. 3;

FIG. 5 is a schematic view showing a first internal structure of the linear compressor according to the embodiment of the present utility model after removing a casing;

FIG. 6 is a schematic view showing a second internal structure of the linear compressor according to the embodiment of the present utility model after removing a casing;

FIG. 7 is a schematic view showing a structure of a piston assembly in a linear compressor according to an embodiment of the present utility model;

FIG. 8 is a cross-sectional view in the direction CC in FIG. 7;

FIG. 9 is a perspective view of a piston assembly in a linear compressor according to an embodiment of the present utility model;

FIG. 10 is a schematic view of a piston assembly of a linear compressor according to an embodiment of the present utility model after unloading the piston;

FIG. 11 is a schematic view of a piston assembly in a linear compressor according to an embodiment of the present utility model after unloading of the piston and ball head structure;

FIG. 12 is a first schematic view of a piston in a linear compressor according to an embodiment of the present utility model;

FIG. 13 is a second schematic view of a piston in a linear compressor according to an embodiment of the present utility model;

FIG. 14 is a schematic view showing the structure of a ball bearing support in a linear compressor according to an embodiment of the present utility model;

fig. 15 is a first structural schematic view of a sound deadening structure in a linear compressor according to an embodiment of the present utility model;

Fig. 16 is a second structural schematic view of a sound deadening structure in a linear compressor according to an embodiment of the present utility model;

fig. 17 is a front view of a sound deadening structure in a linear compressor according to an embodiment of the present utility model;

reference numerals illustrate: 1-a shell, 10-a containing cavity, 11-an elastic supporting leg,

2-Frame body, 21-annular fixing frame, 22-locking piece, 221-locking screw rod, 222-locking nut,

3-Piston cylinder, 31-cylinder body, 32-piston cavity,

4-Piston assembly, 41-piston, 411-converging slot, 412-intake port, 4121-first bore, 4122-second bore, 413-valve plate mounting post, 414-hemispherical recess, 415-fastener attachment post,

42-Piston support, 420-support cavity, 4201-buffer cavity, 421-support body, 4211-support positioning slot, 4212-positioning piece, 422-external screw connection part, 424-ball structure, 4241-ball positioning hole, 425-ball support piece, 4251-annular positioning part, 4252-ball combining ring,

43-Piston valve plate, 431-valve plate body, 432-mounting plate, 433-connecting plate,

44-Fastening structure, 441-fastening support plate, 442-fastening member, 443-compression spring,

5-Rotor assembly, 50-rotor perforation, 51-rotor frame, 511-inner back iron, 5111-inner Hu Tie avoidance groove, 5112-inner back iron protrusion, 512-annular mounting piece, 5121-first annular mounting piece, 5122-second annular mounting piece,

514-An internally threaded connection,

52-A driving magnet, which is arranged on the upper surface of the base plate,

6-Stator assembly, 61-stator frame,

7-Silencing structure, 70-flow channel, 701-flow inlet, 702-flow outlet, 71-silencing tube, 711-tube, 7111-mounting section, 7112-extension, 712-tube through hole, 72-partition plate, 73-silencing cavity, 74-baffle, 75-baffle support post,

8-Connection assembly, 81-elastic member, 811-fixed end, 812-free end,

9-Oil pumping system, 90-oil inlet channel, 91-oil pump, 911-oil pump shell, 912-oil pump piston, 913-oil outlet pipe and 92-oil suction pipe.

Detailed Description

Embodiments of the present utility model are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are illustrative and intended to explain the present utility model and should not be construed as limiting the utility model.

The embodiment of the utility model discloses a linear compressor, which is applied to refrigeration equipment and used as a part of a refrigeration system, wherein the linear compressor is connected between an evaporator and a condenser and used for compressing a refrigerating medium from the evaporator into high-temperature and high-pressure gas, and then the gas enters the condenser for cooling.

It should be understood that the term "refrigeration appliance" is used herein in a generic sense to encompass any manner of refrigeration appliance, such as a freezer, refrigerator, freezer combination, and any make or model of conventional refrigerator. Furthermore, it should be appreciated that the present subject matter is not limited to use in refrigeration appliances. Thus, the present subject matter may be used for any other suitable purpose, such as vapor compression in an air conditioning unit or air compression in an air linear compressor.

The refrigeration equipment is a refrigerator and comprises a box body, a plurality of refrigeration compartments arranged on the box body and a door body arranged on the box body and used for opening or closing the refrigeration compartments. The refrigeration equipment is also provided with a refrigeration system arranged on the box body, and the refrigeration system comprises a linear compressor, a condenser, a throttling device, an evaporator and a refrigerant filled in the circulation loop, which are connected in sequence and form the circulation loop.

Refrigerant in the refrigeration system flows into the linear compressor, which can increase the pressure of the refrigerant. The refrigerant is compressed by the linear compressor and then the temperature of the refrigerant is increased to form high-temperature and high-pressure gas, the temperature of the refrigerant is reduced by the condenser after the refrigerant flows out of the linear compressor, and the refrigerant exchanges heat with the ambient air in the condenser, so that the refrigerant is cooled.

The linear compressor disclosed in this embodiment is operable to increase the fluid pressure within the chamber, and the linear compressor may be used to compress any suitable fluid, such as refrigerant or air. In particular, linear compressors are used as linear compressors for refrigeration systems.

As shown in fig. 1-4, the linear compressor includes a sealed housing 1, the housing 1 preventing or inhibiting leakage or escape of refrigerant from the refrigeration system. The other components of the linear compressor are enclosed in a sealed housing 1. The housing 1 has a receiving cavity 10, and it should be noted that fig. 1 is a schematic diagram of an upper case of the housing 1 after unloading for easy understanding of the present embodiment.

The linear compressor further comprises a frame body 2, a piston cylinder 3 arranged on the frame body 2, a piston assembly 4 and a driving unit; the frame body 2, the piston cylinder 3 arranged on the frame body 2, the piston assembly 4 and the driving unit are all arranged in the accommodating cavity 10;

As shown in fig. 3, the piston cylinder 3 includes a cylinder body 31 and a piston chamber 32 penetrating the cylinder body 31, the cylinder body 31 is fixed to the frame body 2, the piston assembly 4 includes a piston 41, the piston 41 slides in the piston chamber 32, and the piston 41 is cylindrical in shape as a whole and has an axial direction. The driving unit drives the piston 41 to reciprocate in the piston chamber 32, and the piston 41 moves in the axial direction thereof, sucking and compressing the refrigerant in the piston chamber 32 during the reciprocation of the piston 41.

The piston 41 is provided with a piston intake passage through which refrigerant enters the piston chamber 32 to be pressed by the piston 41 during the reciprocating movement. The piston assembly also has a piston valve plate 43, the piston valve plate 43 being movable on the piston 41 to control the communication or closing of the piston intake passage with the piston chamber 32.

It will be appreciated that the linear compressor also has a bleed assembly (not shown) comprising a bleed valve plate disposed on one side of the cylinder 31 and comprising a valve plate for opening or closing the piston chamber 32; a working chamber is formed between the piston 41 and the air release valve plate, refrigerant is introduced into the working chamber and compression is completed in the working chamber, and the space of the working chamber changes along with the movement of the piston 41; the piston 41 is capable of enlarging and compressing the working chamber while reciprocating within the piston chamber 32.

And opening the air release valve plate when the air pressure in the working cavity is increased, releasing the compressed refrigerant and the like in the working cavity from the working cavity by the air release valve plate, and covering the end part of the piston cavity 32 by the air release valve plate after the release is finished. It should be noted that the air leakage component is a mature technology, and the specific structure thereof is not explained here.

As shown in fig. 1-6, the driving unit comprises a stator assembly 6 and a rotor assembly 5, the rotor assembly 5 is matched with the stator assembly 6 and finally drives the piston 41 to move, the rotor assembly 5 can move along the axial direction of the piston 41 relative to the stator assembly 6, and the rotor assembly 5 drives the piston 41 to move in the piston cylinder 3 in the moving process.

In order to facilitate the control of the movement of the piston 3, the piston assembly 4 further comprises a piston holder 42, the piston 41 being mounted and fixed on the piston holder 42, the piston holder 42 being located on the side of the piston 3 facing away from the piston chamber 32. The rotor assembly 5 is matched with the piston support 42, the rotor assembly 5 drives the piston support 42 to move along the axial direction parallel to the piston 41 in the moving process, and the piston support 42 drives the piston 41 to move in the moving process.

As shown in fig. 3, the mover assembly 5 includes a mover frame 51 and a mover through hole 50 provided in the mover frame 51, the mover frame 51 is provided beside the piston cylinder 3, and the piston bracket 42 is inserted through the mover through hole 50 and is mounted and fixed on the mover frame 51. The mover assembly 5 further includes a driving magnet 52 disposed on the mover frame 51, the driving magnet 52 being disposed around the mover frame 51 to form a driving magnet ring.

The stator assembly 6 comprises 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 drive coil is positioned opposite the drive magnet 52 and disposed around the drive magnet 52 to form a drive coil loop, the drive coil loop being disposed coaxially with the drive magnet loop; the electromagnetic force generated after the driving coil is energized drives the driving magnet to reciprocate in the axial direction parallel to the piston 41.

In the prior art, the piston support 42 is generally mounted and fixed on the inner wall of the rotor through hole 50, a first mounting portion is disposed on the outer wall of the piston support 42, a second mounting portion is disposed on the inner wall of the rotor through hole 50, and the mounting and fixing of the piston support 42 is completed through the cooperation of the first mounting portion and the second mounting portion. The prior art method requires that the aperture of the mover perforation 50 not only includes the outer diameter of the piston support 42 but also includes the size of the second mounting portion, and the aperture of the mover perforation 50 is required to be larger than the outer diameter of the piston support 42, which results in that the piston support 42 cannot be better matched with the mover perforation 50 and space is wasted.

In order to avoid the above problem, in this embodiment, the piston support 42 is disposed to penetrate through the rotor through hole and is mounted and fixed at the end of the rotor frame 51, so that the mounting portion on the piston support 42 does not occupy the inner space of the rotor through hole 50, so that the aperture of the whole rotor through hole 50 can be shortened, thereby better matching and attaching with the piston support 42, and making the structure of the whole compressor more compact.

As shown in fig. 3, in an embodiment, the mover frame 51 includes an inner back iron 511 and a pair of ring-shaped mounting members 512 disposed at opposite sides of the inner back iron 511, and the piston holder 42 is screw-coupled to one of the ring-shaped mounting members 512. The driving magnets 52 are provided to the outer wall of the inner back iron 511 and are arranged in the circumferential direction of the inner back iron 511.

As shown in fig. 3 to 6, the outer portion of the inner back iron 511 is entirely columnar and extends in parallel with the sliding direction of the piston 41, and the mover penetrating hole 50 is provided at the center of the inner back iron 511 and penetrates the inner back iron 511 in the axial direction of the inner back iron 511. After the piston assembly 4 is installed and fixed, a part of the piston support 42 is penetrated with a rotor through hole 50; the inner back iron 511 has an overall annular cross section.

A pair of ring-shaped mounting pieces 512 are arranged in the axial direction of the inner back iron 511 and are provided at both ends of the inner back iron 511, respectively. A pair of annular mounting members 512 are a first annular mounting member 5121 and a second annular mounting member 5122 arranged in the axial direction of the piston, respectively, the first annular mounting member 5121 being located on a side farther from the piston cylinder 3 than the second annular mounting member 5122; the piston holder 42 is screwed to the first annular mounting member 5121.

As shown in fig. 3 to 4, the piston holder 42 includes a holder body 421 and an external screw connection portion 422 provided on an outer wall of the holder body 421, and the mover holder body 51 further has an internal screw connection portion 514 provided on an inner wall of the ring-shaped mounting member 512, the internal screw connection portion 514 being screw-fitted with the external screw connection portion 422. The female screw connection portion 422 does not protrude from the inner wall of the mover penetrating hole 50. The internal screw connection 422 does not protrude from the inner wall of the mover penetrating hole 50, so that the mover penetrating hole 50 can be better matched with the piston bracket 42.

Further, the outer diameter size of the piston holder 42 increases as it moves away from the piston cylinder 3. The arrangement of the above-described structure means that the outer diameter dimension of the piston holder 42 gradually decreases as approaching the piston cylinder 3. The outer diameter of the piston support 42 is gradually reduced from the external thread connection part 422 to the piston cylinder 3, so that a larger gap is reserved between the piston support 42 penetrating into the rotor through hole 50 and the rotor through hole 50, and the assembly of the pistons 42 is facilitated.

In this embodiment, as shown in fig. 3 to 4, the outer surface of the driving magnet 52 can be made substantially flush with the outer surface of the inner back iron 511 after the driving magnet 52 is mounted and fixed to the inner back iron 51, and at this time, the driving magnet 52 is embedded in the inner back iron 511, so that the magnetic field from the driving coil can be better applied to the driving magnet 52 during the operation of the linear compressor.

In order to achieve the flush of the outer surface of the driving magnet 52 and the outer surface of the inner back iron 511, a circle of inner back iron avoiding groove 5111 is formed on the outer wall of the inner back iron 511, the inner back iron avoiding groove 5111 is formed on the inner back iron 511 in a concave manner towards the rotor through hole 50, and the inner back iron avoiding groove 5111 is matched with the driving magnet 52 and used for positioning the driving magnet 52. Of course, in other embodiments, the driving magnet 52 may be attached to the outer surface of the inner back iron 511, and the driving magnet 52 protrudes beyond the outer wall of the inner back iron 511 in the radial direction of the inner back iron.

Because the inner back iron avoiding groove 5111 is arranged, the part of the inner back iron 511 provided with the driving magnet 52 is recessed inwards of the rotor through hole 50, and the inner back iron protuberance 5112 protruding towards the rotor through hole 50 is correspondingly formed at the position opposite to the inner back iron avoiding groove 5111 on the inner wall of the rotor through hole 50; the internal threaded connection 514 does not protrude beyond the internal back iron protrusion 5112.

The inner back iron 511 may be formed of or have a plurality of (e.g., ferromagnetic) laminations. A plurality of laminations are circumferentially disposed around and mounted or secured to one another in the circumferential direction of the inner back iron 511. The plurality of laminations can be finally connected and fixed with each other through the annular mounting piece 512 after being distributed along the circumferential direction of the inner back iron 511, and of course, the plurality of laminations can also be installed and fixed through other fixing rings to form the inner back iron 511, and finally the inner back iron 511 is connected and fixed with the annular mounting piece 512.

Since the inner back iron 511 is formed by stacking a plurality of laminated sheets, for the purpose of conveniently realizing the connection and fixation between the laminated sheets, the number of the annular mounting members 512 is two, the two annular mounting members 512 are oppositely arranged at the two ends of the inner back iron 511, and the two annular mounting members 512 connect and fix the plurality of laminated sheets constituting the inner back iron 511 together.

As shown in fig. 1 to 6, in the present embodiment, the stator assembly 6 includes a stator frame 61 and a driving coil (not shown), the stator frame 61 includes an outer back iron, the driving coil is disposed on the outer back iron, the outer back iron is integrally sleeved on the outer side of the mover assembly 5, the stator frame 61 is integrally annular and is wound on the outer side of the inner back iron 51 and is coaxially disposed with the inner back iron 51, and a gap is left between the outer wall of the inner back iron 511 and the stator frame 61. That is, in the radial direction of the inner back iron 511, a gap is left between the outer back iron and the inner back iron 511 so as not to be disturbed by the outer back iron when the inner back iron 511 moves in the axial direction.

In particular embodiments, the outer back iron and/or the drive coil may be disposed extending around the inner back iron 511, e.g., the drive coil is disposed circumferentially around the inner back iron 511 after formation. The drive coil is positioned opposite the drive magnet 52. The drive magnets 52 may face and/or be directly exposed to the drive coils at the outer surface of the inner back iron 511; in the radial direction of the inner back iron 511, a gap is left between the driving magnet 52 and the driving coil.

The driving coil is used to move the inner back iron 511 in the axial direction, for example, a current may be induced in the driving coil through a current source (not shown) to generate a magnetic field that engages with the driving magnet and push the driving magnet 52 to move, and the driving magnet 52 drives the inner back iron 511 to move, and the inner back iron 511 in turn drives the piston assembly 4 to move. The piston 41 is moved in the axial direction to compress the refrigerant in the piston cylinder.

The linear compressor may include various components for allowing and/or regulating operation of the linear compressor, such as a control unit (not shown) in communication with the drive coil or in direct electrical connection. Thus, the control unit may selectively activate the drive coil, thereby causing an induced current to be generated in the drive coil.

In a specific embodiment, as shown in fig. 3 to 6, in order to better realize the mounting and fixing of the mover frame body 61, the frame body 2 includes a pair of ring-shaped fixing frames 21 and a locking member 22, and the locking member 22 clamps and fixes the stator frame body 61 between the pair of ring-shaped fixing frames 21; the linear compressor is also provided with elastic supporting legs 11, and the annular fixing frame 21 is fixed on the shell 1 through the elastic supporting legs 11; each ring-shaped holder 21 is mounted and fixed on the casing 1 by means of two elastic support legs 11.

The locking piece 22 comprises a locking screw 221, a limit nut arranged on the locking screw 221 and a locking nut 222 matched with the locking screw 221, wherein one end of the locking screw 221, which is far away from the limit nut, sequentially penetrates through the two annular fixing frames 21 and is in threaded connection with the locking nut 222, and the stator frame body 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.

It will be appreciated that, for better mounting and fixing of the ring holder 21, a plurality of locking members 22 may be provided, and in this embodiment, four locking members 22 are provided, and four locking members 22 are provided in a ring shape.

The mover assembly 5 is movable in the axial direction of the piston 41, the mover assembly 5 needs to be supported in the radial direction, and the mover assembly 5 needs to be relatively moved with the stator assembly 6 in the axial direction of the piston 41.

In order to achieve the above arrangement of the mover assembly 5, as shown in fig. 5 to 6, in the present embodiment, the linear compressor further has a connection assembly 8, the connection assembly 8 includes a plurality of elastic members 81, the elastic members 81 have fixed ends 811 and free ends 812 disposed opposite to each other, and the fixed ends 811 are fixed to the frame body 2; the free end 812 is fixedly connected to the inner back iron 511, and the elastic member 81 is elastically deformed to move the free end 812 relative to the fixed end 811.

The arrangement of the elastic element 81 not only realizes the fixed support of the rotor assembly 5, but also can enhance the movement of the rotor assembly 5 in the axial direction of the piston 41, and the elastic element 81 accumulates the rebound force after deformation to change the rebound force to work with the magnetic force generated by electromagnetic induction to act on the rotor assembly 5 so as to enable the rotor assembly 5 to move relative to the stator assembly 6.

In order to better make the elastic member 81 not limit 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 back iron 511.

In the embodiment shown in fig. 7-13, the piston support 42 includes a support body 421 and a ball structure 424 disposed on the support body 421, a hemispherical recess 414 adapted to the ball structure 424 is formed on a side of the piston 41 facing away from the piston cavity 32, and the ball structure 424 is movable in the hemispherical recess 414.

The combination is accomplished through the cooperation of bulb structure 424 and hemisphere sunken 414 between piston 41 and the support body 421, can realize producing relative rotation between piston 41 and the support body 421, compares in that piston 41 is complete to be fixed dead on support body 421, and the removal of piston 41 can be better be controlled to the scheme of this embodiment, and piston 41 has great flexibility in the in-process of removal, can reduce the wearing and tearing of piston 41.

In the prior art, the piston 41 is driven by the piston support 42, and because the whole piston support 42 is long-axis, it is difficult to completely control the movement of the piston support 42 along the axial direction of the piston 41, that is, the piston support 42 deviates from the axial direction of the piston 41 in the moving process, or on the premise that the accuracy of the cylinder body 31 of the piston cylinder 3 is insufficient, the piston 41 is easy to cause great abrasion when moving in the piston cylinder 3.

According to the utility model, the piston 41 and the piston support 42 can move in one pass along the axial direction of the piston 41 and simultaneously can generate slight movement in the radial direction, so that the deviation of the sliding direction of the piston 41 caused by the deviation in the moving process of the piston support 42 is reduced, and the abrasion of the piston 41 is reduced.

In addition, since the piston holder 42 and the piston 41 can be moved relatively, the assembly is also facilitated during the assembly of the piston assembly 4 to the mover assembly 5.

It should be noted that the hemispherical recess 414 is not necessarily limited to be hemispherical, and it is intended that the hemispherical recess 414 forms a fit with the ball structure 424 so that the two can move relatively. The hemispherical recesses 414 may be curved, and the ball structures 424 may be curved in other shapes than hemispherical.

The hemispherical recess 414 is preferably fully matched with the shape of the ball head structure 424, so that the hemispherical recess and the ball head structure are better matched and movable, but the precision of the production process is excessively high. And when the production precision is insufficient, the wear of the ball head is easy to occur.

The curvature of the curved surface of hemispherical depressions 414 is no greater than the curvature of the curved surface of ball structures 424 for better use. When both the hemispherical recess 414 and the ball structure 424 are hemispherical, the hemispherical recess 414 has a larger shape to enclose the ball structure 424, that is, the radius of the circle where the curved surface of the hemispherical recess 414 is larger than the radius of the circle where the curved surface of the ball structure 424 is located. In this case, the ball head structure 424, which can be seen as a small sphere, moves within a large sphere-shaped recess.

In the present embodiment, as shown in fig. 8, the ball structure 424 is press-fitted and fixed to the bracket body 421 by the piston 41, and the ball structure 424 is press-fitted and fixed to the end of the bracket body 421.

In particular, the piston assembly 4 also has a fastening structure 44; the fastening structure 44 includes a fastening support plate 441 fixed to the bracket body 421, and a fastening member 442 provided on the fastening support plate 441, a side of the fastening member 442 remote from the fastening support plate 441 being fixed to the piston 41,

The ball structure 424 is compressively positioned at the end of the bracket body 421 under the action of the fasteners 442.

As shown in fig. 8 and 13, the fastening member 442 is a bolt body, the piston 42 is provided with a fastening member connecting post 415 in threaded engagement with the fastening member 442, and the fastening member connecting post 415 is disposed at the bottom of the hemispherical recess 414 and is located at the center of the hemispherical recess 414;

The fastening support plate 441 is provided with a through hole matched with the bolt body, and the end part of the bolt body far away from the piston 41 is provided with a bolt cap; the fastening structure 44 further has a compression spring 443 fitted over the outside of the bolt body and respectively abutting against the bolt cap and the fastening support plate. The compression springs 443 can make the fastening structure 44 more flexible to press the ball structure 424 up onto the bracket body 421.

In the above structure, since the ball structure 424 is pressed against the end of the bracket body 421, the end of the bracket body 421 is generally annular, so that the contact area between the ball structure 424 and the bracket body 421 is limited, and the arrangement of the structure can increase the abrasion of the ball structure 424 during the moving process, thereby weakening the strength of the ball structure 424.

To avoid the above problem, as shown in fig. 8-14, the piston support 42 further includes a ball support 425, where the ball support 425 is positioned and supported on the support body 421, and at least a portion of the ball structure 424 is sleeved outside the ball support 425.

The ball head support 425 is arranged to support the ball head structure 424, after the ball head structure 424 is installed and fixed, the end part of the ball head structure 424 is abutted against the direct body 421, and the ball head structure can be wrapped and attached to the ball head support 425, so that the ball head structure 424 is stably and fixedly supported through contact of a plurality of positions, and the stability of installation and fixation is improved.

In this embodiment, as shown in fig. 8, a bracket cavity 420 is provided in the bracket body 421, a positioning member 4212 is provided on the inner wall of the bracket cavity 420, and a ball head supporting member 425 is inserted into the bracket cavity 420 from the end of the bracket body 421 and abuts against the positioning member 4212.

The ball head structure 424 contacts with the ball head supporting piece 425 at the rear part of the installation and fixation, and the end part of the ball head structure 424 is abutted against the end part of the supporting body 423, and the arrangement of the structure enables the ball head structure 424 to have more supporting positions, so that more stable installation and fixation are realized.

Specifically, as shown in fig. 14, the ball support 425 has an annular positioning portion 4251 positioned on the bracket body 421 and a ball coupling ring 4252 coaxially provided with the annular positioning portion 4251;

The bracket body 421 is provided with a bracket positioning groove 4211 adapted to the annular positioning part 4251, the positioning part forms the bottom of the bracket positioning groove 4211, the annular positioning part 4251 penetrates into the bracket positioning groove 4211 after the ball head supporting part 425 is installed and fixed, and the end part of the annular positioning part 4251 is abutted against the positioning part.

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

In this embodiment, the outer diameter of the ball joint ring 4252 is smaller than the outer diameter of the annular positioning portion 4251, and the outer diameter of the ball joint ring 4252 gradually decreases with distance from the annular positioning portion 4251.

In use, refrigerant enters the piston chamber 32 through the piston inlet passage in the piston 41, and the piston assembly 4 further includes a bracket chamber 420 in communication with the piston inlet passage for better refrigerant delivery. In the present embodiment, the bracket cavity 420 is disposed on the piston bracket 42, and in other embodiments, when there is no piston bracket 42, the bracket cavity 420 may also exist with other structures as carriers, and the bracket cavity 420 is only used as a flow passage for the refrigerant to be transferred into the piston intake passage.

After the refrigerant is sucked into the flow channel, the piston valve plate 43 is opened to conduct the piston air inlet channel and the piston cavity, so that the refrigerant is sucked into the piston cavity for compression of the piston, and after the refrigerant enters the piston valve plate 43, the piston valve plate 43 is closed to close the conduction between the piston air inlet channel and the piston cavity.

In the prior art, in order to ensure that a sufficient air inflow generally comprises a plurality of air inlets, the arrangement of the plurality of air inlets requires the piston valve plate 43 to cover the plurality of air inlets at the same time, so that certain requirements are made on the size of the piston valve plate 43, and the difficulty in opening the piston valve plate 43 is necessarily increased due to the increase of the size of the piston valve plate 43.

In order to better realize the opening of the piston valve plate 43, as shown in fig. 8-13, in this embodiment, the piston air intake channel includes a converging slot 411 disposed on the piston 41 and a plurality of air intake holes 412 communicating with the converging slot 411, the converging slot 411 is disposed on a 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 slot 411.

In this embodiment, different air inlets 412 are converged through the setting of the converging slot 411, and the corresponding design can be performed on the piston valve plate 43 through the design of the opening shape of the converging slot 411, so that the problem that the structure of the piston valve plate 43 is limited by the number and distribution of the air inlets 412 is solved, and the piston valve plate 43 can be better designed to realize better opening of the piston valve plate 43.

In a specific embodiment, as shown in fig. 12 to 13, the air intake hole 412 includes a first hole 4121 located at the bottom of the converging slot 411 and a second hole 4122 located at the sidewall of the converging slot 411. In this embodiment, the air inlet holes 412 are simultaneously disposed at the bottom and the side wall of the converging slot 411, so that the air inlet holes 412 have a larger flow area, and the flow rate of the refrigerant is not affected when the piston valve plate 43 is designed. The design of the converging slot 411 in this embodiment actually converts the circular air inlet into an annular air outlet, and the annular air outlet can be controlled more conveniently than the circular air inlet.

In this embodiment, as shown in fig. 12, a plurality of air intake holes 412 are provided, and the plurality of air intake holes 412 are annularly arranged. The converging slot 411 is also integrally arranged in an annular shape, a valve plate mounting column 413 is arranged at the center of the piston 41, and the converging slot 411 is arranged around the valve plate mounting column 413; the outer wall of the valve sheet mounting column 413 forms the inner wall of the converging slot 411; the valve plate body 431 is also disposed in an annular shape and is adapted to the annular converging slot 411. The valve plate body 431 covers the opening of the converging slot 411 so that the piston flow channel and the piston cavity 32 are closed, and when the valve plate body 431 leaves the opening of the converging slot 411, the opening of the piston flow channel and the piston cavity 32 is realized.

It is understood that the piston valve plate 43 further has a mounting plate 432 fixed to the valve plate mounting post 413 and a connecting plate 433 connected to the mounting plate 432 and the valve plate body 431, and the connecting plate 433 can be elastically deformed to drive the valve plate body 431 out of covering the converging slot 411.

When the air pressure of the refrigerant in the piston flow channel increases, the valve plate body 431 is pushed to move in a direction away from the converging slot 411 to open the converging slot 411, at this time, the connecting sheet 433 generates elastic deformation, and the connecting sheet 433 continues to rebound, so that the valve plate body 431 is driven to rebound after the air pressure in the piston flow channel decreases, and the closing of the converging slot 411 is realized.

In the practical use process, the size of the connecting sheet 433 and the size of the valve sheet body 431 are mutually influenced, when the size of the valve sheet body 431 is larger, the size of the connecting sheet 433 is correspondingly reduced, so that the opening difficulty of the piston valve sheet 43 is increased, and it is noted that the size mainly refers to the length of the connecting sheet 433 which can be extended between the valve sheet body 431 and the mounting sheet 432. When the size of the valve plate body 431 is smaller, the size of the connecting sheet 433 can be correspondingly increased, so that the elastic deformation of the connecting sheet 433 can be realized more conveniently, and the connecting sheet 433 can be opened more conveniently.

In this embodiment, different air inlets 412 are converged together through the setting of the converging slot 411, so that the valve plate body 431 which originally covers a plurality of air inlets 412 simultaneously is changed into a valve plate body which only needs to cover the converging slot 411, the setting of the valve plate body 431 can be better realized when the piston flow channel is controlled conveniently, the valve plate body 431 has a narrower width, and the convenient control of opening of the piston valve plate 43 is realized.

As shown in fig. 9, the connection piece 433 may be provided in plurality, and the plurality of connection pieces 433 are arranged in a ring shape centering on the mounting piece 432. In this embodiment, two connection pieces 433 are provided, and the two connection pieces 433 are arranged symmetrically with the mounting piece 432 as a symmetry point center. In the present embodiment, since the valve plate body 431 and the converging groove are also configured in an annular shape, and the mounting piece 432 is also configured in a circular shape, the overall shape of the piston valve plate 43 is a center-symmetrical pattern. The arrangement of the structure can conveniently realize the installation and fixation of the piston valve plate 43, and the piston valve plate 43 is not excessively limited in the installation and fixation process.

Further, in order to better realize control of the piston flow channel, the converging slot 411 is provided such that the opening of the converging slot 411 is gradually narrowed away from the bottom of the converging slot 411. The gradual narrowing of the opening of the converging slot 411 can achieve better control of opening of the converging slot 411.

In order to reduce noise, as shown in fig. 8-17, the linear compressor further includes a silencing structure 7, and in this embodiment, the silencing structure 7 is disposed in the bracket cavity 420, that is, the silencing is completed before the refrigerant enters the flow channel.

In particular, as shown in fig. 15-17, the sound attenuating structure 7 includes a sound attenuating tube 71 having a flow passage 70, the flow passage 70 communicating with the bracket cavity 420, the flow passage 70 having a flow inlet 701 and a flow outlet 702, the flow outlet 702 of the flow passage being exposed directly to the bracket cavity 420. The silencing pipe 71 comprises a pipe body 711, the silencing structure 7 further comprises a plurality of partition plates 72 arranged on the outer wall of the pipe body 711, the partition plates 72 are distributed along the axial direction of the pipe body 711, the partition plates 72 are attached to the inner wall of the bracket cavity 420, a silencing cavity 73 is formed between two adjacent partition plates 72, and a pipe body through hole 712 communicated with the flow channel 70 and the silencing cavity 73 is formed in the pipe body 711.

Each of the sound deadening chambers 73 is provided with a plurality of pipe body through holes 712, and the plurality of pipe body through holes 712 are arranged in the circumferential direction of the pipe body 711. In this embodiment, two pipe through holes 712 are correspondingly disposed in one silencing cavity 73, and the two pipe through holes 712 are disposed on two opposite sides of the pipe 711.

It should be noted that each partition plate 72 extends along the circumferential direction of the pipe body 711, and the partition plates 72 are integrally sleeved outside the pipe body 711, and a sound deadening chamber 73 is formed between two adjacent partition plates 72, an outer wall of a part of the pipe body 711, and an inner wall of a part of the bracket chamber 420.

In this embodiment, the silencing cavities 73 are provided with a plurality of silencing cavities 73, the silencing cavities 73 are arranged along the axial direction of the pipe body 711, different silencing cavities 73 are different in size, and different silencing cavities 73 are used for eliminating different noises, so that a better noise reduction effect is achieved.

The refrigerant mainly flows along the axial direction of the pipe body 711 in the flowing process, and flows in the pipe cavity of the pipe body 711 as a part of the flow channel 70, the refrigerant enters different silencing cavities 73 through the pipe body through holes 712 in the flowing process, and the silencing cavities 73 play a certain buffering role on the flowing refrigerant, so that the noise reduction effect can be achieved.

In this embodiment, the opening of the through hole 712 is elongated, and the opening of the through hole 712 extends in a first direction parallel to the axial direction of the pipe 711, that is, the opening of the through hole 712 extends in a direction parallel to the axial direction of the pipe 711.

The opening shape of the tube through hole 712 is actually parallel to the flow direction of the refrigerant, so that the refrigerant can smoothly enter the silencing cavity 73, the silencing cavity 73 has a better silencing effect, and vortex is easily formed after the refrigerant enters the silencing cavity 73, so that the silencing effect can be further enhanced by the formed vortex.

In the present embodiment, the opening shape of the tube body through-hole 712 is rectangular in shape as a whole and has a length direction and a width direction, and 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.

In this embodiment, since the outer diameter of the piston holder 42 gradually increases as it moves away from the piston 41, the size of the holder cavity 420 provided in the piston holder 42 also gradually increases, and the distance between the adjacent two partition plates 72 gradually increases as it moves away from the piston 41.

In one embodiment (not shown) the lumen is the flow channel 70, the flow inlet 701 and the flow outlet 702 are disposed on opposite sides of the tube body 711, and the opening direction of the flow outlet 702 is oriented in the axial direction of the tube body 711, i.e. toward the piston 41, so that the refrigerant fluid flowing out of the flow channel 70 directly impacts the piston 41, which is not only liable to damage the piston valve plate 43 on the piston 41, but also liable to generate a loud noise.

Further, in order to avoid the occurrence of the above-described problem, in another embodiment, as shown in fig. 15 to 17, the silencing structure 7 includes a silencing pipe 71 having a flow passage 70, and the silencing pipe 71 has a flow outlet 702 exposed toward the bracket cavity 420 at a position close to the piston 41, the opening direction of the flow outlet 702 being inclined with respect to the axial direction of the piston 41.

Specifically, the opening direction of the flow outlet 702 of the flow channel 70 is not along the axial direction of the piston 41, so that the influence on the piston valve plate 431 on the piston 41 can be avoided, meanwhile, as the whole flow channel of the refrigerant is bent to a certain extent, the flow speed can be buffered, and the larger noise generated in the process of transmitting the refrigerant can be effectively reduced.

In a specific embodiment, the opening direction of the flow outlet 702 is perpendicular to the axial direction of the piston 41, i.e. the opening direction of the flow outlet 702 is along the radial direction of the tube 711. The flow outlets 702 are provided in plurality, and the plurality of flow outlets 702 are arranged in the circumferential direction of the silencer duct 71.

To achieve the above arrangement of the flow outlet 702, the silencer duct 71 includes a duct body 711 having a duct chamber, a baffle 74, and a baffle support post 75;

The tube body 711 is disposed to extend in parallel with the axial direction of the piston 41 and has a proximal end and a distal end disposed opposite to each other, the proximal end and the distal end of the tube body 711 being closer to the piston 41; the baffle 74 is fixed at the proximal end of the tube body 711 by a baffle support column 75 and the baffle 74 is opposite to the lumen position; the flow outlet 702 of the flow channel 70 is disposed between the flap 74 and the proximal end of the tube 711.

The flap 74 is in effect shielded at the outlet of the lumen to avoid the outlet of the lumen directly against the piston 41.

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

The flow outlet 702 can be considered as a lateral opening formed in the sidewall of the tube 711, the proximal end of the tube 711 being plugged, and a radially directed opening formed in the sidewall of the tube 711.

When the flow outlet 702 is opened along the radial direction of the pipe body 711, the position of the flow outlet 702 and the position of the pipe body through hole 712 are staggered in the axial direction of the pipe body 711, that is, the positions of the flow outlet 702 and the pipe body through hole 712 in the axial direction of the pipe body 711 are not opposite, and the two are not in the same straight line, so that the strength of the pipe body 711 can be better increased by the arrangement of the structure.

The refrigerant enters the buffer chamber 4201 after flowing from the flow outlet 702 of the flow passage 70, and the buffer chamber 4201 is surrounded by the bracket chamber 420, the partition plate 72, and the piston 41 as a part of the bracket chamber 420. The position in the holder cavity 420 where the partition plate 72 is provided forms a mounting cavity opposite to the buffer cavity 4201, and the sound deadening cavity 73 is actually a part of the mounting cavity, the partition plate 72 and the pipe body 711 dividing the mounting cavity into different chambers to form the sound deadening cavity 73.

After the refrigerant enters the buffer cavity, the air pressure in the buffer cavity is continuously increased, and after the air pressure reaches a certain height, the piston valve plate 43 is opened, so that the refrigerant in the buffer cavity flows into the piston cavity 32.

In the prior art, the partition plates 72 are generally arranged on the entire tube body 711 along the axial direction of the tube body 711, and the arrangement of the structure compresses the volume of the buffer chamber 4201, so that more 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.

To avoid the above problem, in one embodiment, the partition plate 72 is integrally provided on the pipe body 711 at a position relatively distant from the piston 41.

The tube body 711 is disposed to extend in parallel with the axial direction of the piston 41 and has a proximal end and a distal end disposed opposite to each other, the proximal end being located near the piston 41 with respect to the distal end, and the flow outlet 702 being disposed at the proximal end of the tube body 711; the divider plate 72 is integrally disposed on the tube body relatively near the distal end.

The pipe body 711 has a mounting section 7111 and an extension section 7112 arranged in parallel in the axial direction of the piston, the extension section 7112 is provided to extend from an end of the mounting section 7111 toward the piston 41, and the partition plate 72 is provided on the mounting section 7111;

a buffer chamber 4201 is formed between the outer wall of the extension 7112, the piston 41, the partition plate 72 and a portion of the inner wall of the bracket chamber 420, the buffer chamber 4201 communicates with the flow channel 70, and the flow outlet 701 is exposed toward the buffer chamber 4201.

The piston valve plate 43 is arranged on the side of the piston 41 facing away from the damping chamber 4201, i.e. on the side of the piston 41 facing away from the sound damping structure 7. The refrigerant passes through the flow passage 70 and enters the buffer chamber 4201, the air pressure in the buffer chamber 4201 increases, and the piston valve plate 43 is lifted up after the air pressure increases, thereby opening the piston intake passage.

In the prior art, because the volume in the buffer chamber 4201 is larger, the refrigerant stored in the buffer chamber 4201 is less difficult to push and open the piston valve plate 43, so that the piston valve plate 43 is generally made to be very thin to avoid the above problems, and the structure is easy to damage the piston valve plate 43, so that the piston valve plate 43 fails. In this embodiment, the space in the buffer cavity 4201 is increased by changing the distribution of the partition plates 72 on the muffler 71, and more refrigerant can be accumulated in the buffer cavity 4201 due to the increase of the space in the buffer cavity 4201, so that a larger force can be formed to push the piston valve plate 43 to open, the setting of the piston valve plate 43 is conveniently realized, and meanwhile, the thickness of the piston valve plate 43 can be increased to improve the stability of the piston valve plate 43 in the operation process.

The compressor also has an oil pumping system 9, the oil pumping system 9 providing lubrication oil in the piston chamber 32.

The oil pumping system 9 comprises an oil pump 91, an oil inlet channel 90 and an oil suction pipe 92, wherein the oil pump 91 is provided with an oil inlet and an oil outlet which are oppositely arranged, and the oil inlet channel 90 is communicated with the oil outlet of the oil pump 91 and the piston cavity 32; the oil suction pipe 92 is arranged at the oil inlet of the oil pump 91, the oil suction pipe 92 extends towards the bottom of the accommodating cavity 10, and the inlet of the oil suction pipe 92 is relatively positioned near the center of the shell 1.

The central position of shell 1 is the lowest position of holding chamber 10, therefore lubricating oil can assemble this after spouting holding chamber 10, through the setting of inhaling oil pipe 92 and with inhaling the import setting of oil pipe 92 in the central position that is close to shell 1 can be more convenient for inhale of lubricating oil, improves oil feed efficiency.

The cross section of the shell 1 along the horizontal direction has a length direction and a width direction, and the inlet of the oil suction pipe 92 is relatively positioned at the center of the shell 1 in the width direction.

The oil pump 91 includes an oil pump housing 911, an oil pump piston 912 disposed within the oil pump housing 911; the oil pump piston 912 slides in the axial direction of the oil pump housing 911, and the oil pump 91 further includes an oil outlet pipe 913, the oil outlet pipe 913 being a part of the oil inlet passage 90;

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.

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 further includes a pair of springs provided at opposite sides of the oil pump piston 912, the pair of springs being provided in the first chamber and the second chamber, respectively, and the oil pump piston 912 further has a communication hole communicating the first chamber and the second chamber.

The compressor further has a mixed liquid disposed in the housing 1, the mixed liquid including a mixed liquid of lubricating oil and a 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 arranged 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.

In order to conveniently realize the suction of the mixed liquid in the prior art, the oil pump 91 is generally immersed in the mixed liquid, the oil pump 91 can vibrate in the use process, and when the oil pump 91 is immersed in the mixed liquid, the vibration process of the oil pump 91 can generate larger noise. In this embodiment, the oil pump 91 is disposed above the surface of the mixed liquid, and the mixed liquid is sucked through the oil suction pipe 92, so that noise generated in the use process of the compressor can be effectively reduced.

The utility model further discloses refrigeration equipment, which comprises a box body and a refrigeration system arranged on the box body, wherein the refrigeration system comprises a linear compressor, a condenser, a throttling device and an evaporator which are sequentially connected in series. The linear compressor is the linear compressor. The refrigeration equipment of the embodiment of the utility model can be a refrigerator, a freezer, a wine cabinet or the like.

While the foregoing is directed to embodiments of the present utility model, other and further embodiments of the utility model may be devised without departing from the basic scope thereof, and the scope thereof is determined by the claims that follow.

Claims (10)

1. A linear compressor, comprising: the device 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 also comprises a bracket cavity communicated with the piston air inlet channel and a silencing structure arranged in the bracket cavity,

The silencing structure comprises a silencing pipe with a flow channel, wherein the flow channel is communicated with the bracket cavity, the silencing pipe comprises a pipe body and a plurality of partition plates arranged on the outer wall of the pipe body, the partition plates are arranged along the axial direction of the pipe body, the partition plates are attached to the inner wall of the bracket cavity, a silencing cavity is formed between two adjacent partition plates, and a pipe body through hole for communicating the flow channel with the silencing cavity is formed in the pipe body; the whole opening of the tube body through hole is strip-shaped and extends towards the axial direction parallel to the tube body.

2. The linear compressor of claim 1, wherein: the opening of the pipe body through hole is integrally formed and provided with a length direction and a width direction, and the length direction of the pipe body through hole is parallel to the axial direction of the pipe body.

3. The linear compressor of claim 1, wherein: the pipe body through holes are arranged in a plurality and circumferentially distributed mode along the pipe body.

4. The linear compressor of claim 1, wherein: each silencing cavity is provided with a corresponding pipe body through hole communicated with the flow channel, and the pipe body through holes in different silencing cavities are distributed along the axial direction parallel to the pipe body.

5. The linear compressor of claim 1, wherein: the outer diameter of the piston support gradually increases along with the distance from the piston, and the distance between two adjacent separation plates also gradually increases.

6. The linear compressor of claim 1, wherein: the piston assembly further comprises a piston support, the piston support comprises a support body and a ball head structure arranged on the support body, the support cavity is arranged on the support body, a hemispherical recess matched with the ball head structure is formed on one side, away from the piston cavity, of the piston, and the ball head structure can move in the hemispherical recess;

The piston support further comprises a ball head support piece, the ball head support piece is positioned and supported on the support body, and at least part of the ball head structure is sleeved outside the ball head support piece.

7. The linear compressor of claim 1, wherein: the linear compressor is also provided with a gas leakage component, and the gas leakage component comprises a gas leakage valve plate which is arranged at one side of the cylinder body and is used for opening or closing the piston cavity; a working cavity is formed between the piston and the air leakage valve plate, and the driving unit drives the piston to reciprocate in the piston cavity so as to enlarge or compress the working cavity;

The piston assembly further comprises a piston valve plate which moves on the piston to control the connection or disconnection of the piston air inlet channel and the working cavity.

8. The linear compressor of claim 7, wherein: the piston air inlet channel comprises a converging groove and a plurality of air inlet holes communicated with the converging groove, the converging groove is arranged on one side of the piston facing the working cavity, and the piston valve plate comprises a valve plate body matched with the opening of the converging groove.

9. The linear compressor of claim 1, wherein: the driving unit comprises a stator assembly and a rotor assembly, the piston assembly further comprises a piston support, the piston is fixed on the piston support, and the rotor assembly drives the piston support to reciprocate along the axial direction of the piston;

The stator component is arranged on the frame body and matched with the rotor component to drive the rotor component to move;

The rotor assembly comprises an inner back iron and a driving magnet arranged on the outer wall of the inner back iron, and the driving magnet is annularly arranged on the outer wall of the inner back iron to form a driving magnet ring;

The stator assembly comprises a stator frame body and a driving coil arranged on the stator frame body, and the stator frame body is fixed on the frame body; the driving coil is opposite to the driving magnet in position and surrounds the driving magnet to form a driving coil ring, and the driving coil ring and the driving magnet ring are coaxially arranged; the electromagnetic force generated after the driving coil is electrified drives the driving magnet to reciprocate along the axial direction of the piston.

10. A refrigeration device, characterized by: comprising a tank and a refrigeration system provided on the tank, said refrigeration system comprising a linear compressor according to any one of claims 1 to 9.