WO2017024867A1

WO2017024867A1 - Compressor, heat exchanger, and operating method of compressor

Info

Publication number: WO2017024867A1
Application number: PCT/CN2016/084330
Authority: WO
Inventors: 胡余生; 杜忠诚; 徐嘉; 杨森; 任丽萍; 孔令超; 张荣婷; 梁社兵; 邓丽颖; 丁宁
Original assignee: 珠海格力节能环保制冷技术研究中心有限公司
Priority date: 2015-08-07
Filing date: 2016-06-01
Publication date: 2017-02-16
Also published as: CN106438356B; CN106438356A

Abstract

A compressor, comprising: an upper flange (50); a lower flange (60); at least two cylinders (20), wherein the at least two cylinders (20) are sandwiched between the upper flange (50) and the lower flange (60), and any two adjacent cylinders (20) operate independently; a rotation shaft assembly, wherein the rotation shaft assembly passes through the upper flange (50), the cylinders (20) and the lower flange (60) sequentially and comprises sub-rotation shafts (10) disposed correspondingly to each of the at least two cylinders (20), the sub-rotation shaft (10) and the cylinder (20) to which the sub-rotation shaft corresponds are eccentrically disposed and the eccentric distance is fixed; piston units (30), wherein the piston units (30) have variable volume chambers (31) corresponding to each of the cylinders (20), the piston units (30) are pivotably disposed in the cylinders (20) and at least one of the sub-rotation shafts (10) is drivingly connected to the piston units (30) to change the volume of the variable volume chamber (31). Also disclosed are a heat exchanger comprising the compressor and an operating method of the compressor. The compressor has little vibration, and thus ensures a regular volume variation of the variable volume chamber, reduces the clearance volume and therefore improves the operational stability and operational reliability of the compressor.

Description

Compressor, heat exchange equipment and compressor operating method

Technical field

The invention relates to the technical field of heat exchange systems, in particular to a compressor, a heat exchange device and a method for operating a compressor.

Background technique

Compressors of the prior art include compressors, expanders, and the like. Take the compressor as an example.

In the prior art piston rotor, the position of the center of mass of the sub-rotary shaft and the cylinder during the movement is varied. The motor drives the crankshaft to output power, and the crankshaft drives the piston to reciprocate in the cylinder to compress the gas or the liquid to perform work for the purpose of compressing the gas or the liquid.

The traditional piston compressor has many defects: due to the presence of the suction valve piece and the exhaust valve piece, the suction and exhaust resistance are increased, and the suction and exhaust noise is increased; the cylinder of the compressor is subjected to the lateral force. Large, lateral force does useless work, reducing compressor efficiency; crankshaft drives the piston to reciprocate, the eccentric mass is large, resulting in large compressor vibration; the compressor drives one or more pistons through the crank linkage mechanism, the structure is complex; the crankshaft and The piston is subjected to a large lateral force, and the piston is easily worn, resulting in a decrease in piston sealing performance. Moreover, the existing compressor has a volumetric efficiency due to the existence of a clearance volume, a large leak, and the like, and it is difficult to further improve.

Moreover, the circular motion of the centroid of the eccentric portion of the piston compressor produces a centrifugal force of constant size and direction, which causes the vibration of the compressor to be intensified.

Summary of the invention

SUMMARY OF THE INVENTION A primary object of the present invention is to provide a method for operating a compressor, a heat exchange device, and a compressor to solve the problem of the prior art compressor having unstable motion, large vibration, and residual volume.

In order to achieve the above object, according to an aspect of the invention, a compressor is provided, comprising: an upper flange; a lower flange; at least two cylinders, at least two cylinders sandwiched between an upper flange and a lower flange Any two adjacent cylinders work independently of each other; the rotating shaft assembly, the rotating shaft assembly sequentially passes through the upper flange, the cylinder and the lower flange, and the rotating shaft assembly includes a sub-rotating shaft corresponding to each of the at least two cylinders The axis of the sub-rotating shaft is eccentrically disposed with the axis of the cylinder corresponding to the sub-rotating shaft and the eccentric distance is fixed; the piston assembly and the piston assembly have variable volume chambers corresponding to each cylinder, and the piston assembly is pivotally disposed in the cylinder And at least one sub-rotary shaft is drivingly coupled to the piston assembly to change the volume of the variable volume chamber.

Further, the piston assembly includes: a piston sleeve that is pivotally disposed in the cylinder; at least two pistons that are slidably disposed within the piston sleeve to form a variable volume chamber, and the variable volume chamber is located in a sliding direction of the piston.

Further, the cylinder, the sub-rotating shaft and the piston are each two, and one sub-rotating shaft is a driving shaft, and extends through the upper flange into a cylinder near one side of the upper flange, and is movably connected with the piston in the cylinder; The sub-shaft is a passive shaft that extends through the lower flange into a cylinder near the side of the lower flange and is movably coupled to the piston in the cylinder.

Further, the drive shaft is driven to rotate by the motor, and the driven shaft is driven indirectly by the drive shaft.

Further, the piston has a sliding hole disposed along the axial direction of the sub-rotating shaft, and the sub-rotating shaft passes through the sliding hole, and the piston engaged with the driving shaft rotates with the driving shaft under the driving of the driving shaft while being perpendicular to the driving shaft. The axial direction reciprocates in the piston sleeve; the piston engaged with the passive shaft rotates with the piston sleeve and drives the passive shaft to rotate under the driving of the piston sleeve, and the piston engaged with the passive shaft is in the piston sleeve along the axis perpendicular to the passive shaft. Slide back and forth.

Further, the sliding hole is a long hole or a waist hole.

Further, the piston has a pair of arcuate surfaces symmetrically disposed along the median plane of the piston, the arcuate surface being adapted to fit the inner surface of the cylinder, and the radius of curvature of the arcuate surface of the arcuate surface is equal to twice the inner diameter of the cylinder.

Further, the piston is cylindrical.

Further, the piston sleeve has a guiding hole disposed in a radial direction of the piston sleeve. The guiding holes are at least two, and each of the guiding holes is correspondingly provided with a piston, and the piston is slidably disposed in the guiding hole to reciprocate linearly.

Further, the axes of each of the guide holes are parallel.

Further, a partition is formed between two adjacent guide holes in the piston sleeve, and the oil passage hole for connecting the adjacent two guide holes is opened in the partition.

Further, the axis of the oil passage hole is parallel to the axis of the sub-rotation shaft.

Further, the orthographic projection of the guiding hole at the lower flange has a pair of parallel straight segments, and a pair of parallel straight segments are formed by projecting a pair of parallel inner wall faces of the piston sleeve, and the piston has a pair with the guiding holes. The parallel inner wall faces are shaped to fit and slip fit to the outer profile.

Further, the first thrust surface of the piston sleeve facing the lower flange side is in contact with the surface of the lower flange.

Further, the sub-rotating shaft has a sliding section that is in sliding engagement with the piston assembly, the slip section is located at one end of the sub-rotating shaft near the cylinder, and the slip section has a slip fit surface.

Further, the slip fit surfaces are symmetrically disposed on both sides of the slip segment.

Further, the sliding mating surface is parallel to the axial plane of the sub-rotating shaft, and the sliding mating surface and the inner wall surface of the sliding hole of the piston are slidably engaged in an axial direction perpendicular to the sub-rotating shaft.

Further, the sub-rotating shaft has a lubricating oil passage including an internal oil passage disposed inside the sub-rotating shaft, an external oil passage disposed at the slip fitting surface, and an oil passage hole communicating the internal oil passage and the external oil passage.

Further, adjacent two cylinders are disposed concentrically with each other.

Further, the axis of the upper flange is eccentric with the axis of the cylinder disposed on the side close to the upper flange.

Further, the axis of the lower flange is eccentric with the axis of the cylinder disposed on the side close to the lower flange.

Further, the compressor further includes a support plate disposed on an end surface of the lower flange away from the cylinder side, and the support plate is disposed concentrically with the lower flange to support the rotating shaft assembly, and the support plate has a support for supporting the rotating shaft assembly. The second thrust surface.

Further, the cylinder wall of each cylinder has a compressed intake port and a first compressed exhaust port, and when the piston assembly is in the intake position, the compressed intake port is electrically connected to the variable volume chamber; when the piston assembly is in the exhaust position The variable volume chamber is electrically connected to the first compressed exhaust port.

Further, the inner wall surface of the cylinder wall has a compressed intake buffer groove, and the compressed intake buffer groove communicates with the compressed intake port.

Further, the compressed intake buffer groove has an arc segment in a radial plane of the cylinder, and the compressed intake buffer groove extends from a side of the compression intake port to a side of the first compression exhaust port.

Further, the cylinder wall of each cylinder has a second compressed exhaust port, and the second compressed exhaust port is located between the compressed intake port and the first compressed exhaust port, and during the rotation of the piston assembly, the piston assembly Part of the gas is first discharged through the second compressed exhaust port and then discharged from the first compressed exhaust port.

Further, the compressor further includes an exhaust valve assembly disposed at the second compressed exhaust port.

Further, the outer wall of the cylinder wall is provided with a receiving groove, and the second compressed exhaust port penetrates the bottom of the receiving groove, and the exhaust valve assembly is disposed in the receiving groove.

Further, the exhaust valve assembly includes: an exhaust valve piece disposed in the receiving groove and blocking the second compressed exhaust port; and a valve plate baffle, the valve plate baffle is stacked on the exhaust valve plate.

According to another aspect of the present invention, there is provided a heat exchange apparatus including a compressor, the compressor being the above compressor.

According to another aspect of the present invention, there is provided a method of operating a compressor, comprising: rotating a sub-rotary shaft about an axis O _{1 of a} sub-rotary shaft; rotating the cylinder about an axis O _{2 of the} cylinder, and axially-centering the cylinder of the sub-rotating shaft The shaft center is eccentrically disposed and the eccentric distance is fixed; the piston of the piston assembly rotates with the sub-rotation shaft under the driving of the sub-rotation shaft and simultaneously reciprocates in the piston sleeve of the piston assembly in the axial direction perpendicular to the sub-rotation shaft.

Further, the running method adopts the principle of the cross slider mechanism, wherein the piston acts as a slider, and the slip matching surface of the sub-rotating shaft serves as the first connecting rod l ₁ and the guiding hole of the piston sleeve as the second connecting rod l ₂ .

Applying the technical solution of the present invention, any two adjacent cylinders work independently of each other, and the eccentricity distance is fixed by eccentrically setting the axis of the sub-shaft in the rotating shaft assembly and the axis of the cylinder corresponding to the sub-rotating shaft, thereby The sub-rotary shaft and the cylinder are rotated around the respective axes during the movement, and the centroid position is unchanged, so that the piston assembly can stably and continuously rotate when moving in the cylinder, thereby effectively alleviating the vibration of the compressor and ensuring the variable volume. The volume change of the cavity has a regularity, and the clearance volume is reduced, thereby improving the operational stability of the compressor, thereby improving the operational reliability of the heat exchange device.

DRAWINGS

The accompanying drawings, which are incorporated in the claims of the claims In the drawing:

Figure 1 is a schematic view showing the structure of a compressor in the present invention;

Figure 2 shows an exploded view of the pump body assembly of the present invention;

Figure 3 is a schematic view showing the installation relationship of the sub-rotating shaft, the upper flange, the cylinder and the lower flange in the present invention;

Figure 4a shows a schematic view of the internal structure of Figure 3;

Figure 4b shows a structural view of another angle of Figure 4a;

Figure 5 is a schematic view showing the installation relationship of the exhaust valve assembly and the cylinder in the present invention;

Figure 6 is a schematic view showing the structure of the sub-rotating shaft on the side close to the upper flange in the present invention;

Figure 7 is a schematic view showing the internal structure of the sub-rotating shaft of Figure 6;

Figure 8 is a schematic view showing the structure of the sub-rotating shaft near the side of the lower flange in the present invention;

Figure 9 is a schematic view showing the internal structure of the sub-rotating shaft of Figure 8;

Figure 10 is a schematic view showing the structure of a piston in the present invention;

Figure 11 is a schematic view showing the structure of another angle of the piston of Figure 10;

Figure 12 is a schematic view showing the structure of a piston sleeve in the present invention;

Figure 13 is a cross-sectional view showing a piston sleeve in the present invention;

Figure 14 is a view showing the structure of the upper flange in the present invention;

Figure 15 is a view showing the structure of the lower flange in the present invention;

Figure 16 is a schematic view showing the eccentric relationship between the axis of the sub-rotating shaft on the side of the lower flange and the axis of the piston sleeve at the lower flange of Figure 15;

Figure 17 is a view showing the working state of the piston in the present invention when it is ready to start inhaling;

Figure 18 is a view showing the working state of the piston in the present invention in the process of inhalation;

Figure 19 is a view showing the working state of the piston in the present invention when the suction is completed;

Figure 20 is a view showing the working state of the piston in the present invention when it is in gas compression and is exhausted from the second compressed exhaust port;

Figure 21 is a view showing the working state of the piston in the exhausting process of the present invention;

Figure 22 is a view showing the working state of the piston in the present invention when the exhaust gas is completed;

Figure 23 is a view showing the working state of the piston in the present invention when the exhaust gas is completed;

Fig. 24 is a view showing the operation of the compressor in the present invention.

Wherein, the above figures include the following reference numerals:

10, sub-rotating shaft; 11, slip section; 111, slip fit surface; 13, lubricating oil passage; 14, oil passage hole; 15, the axis of the sub-rotation shaft near the lower flange side; 20, cylinder; , compressed air inlet; 22, first compressed exhaust port; 23, compressed intake buffer tank; 24, second compressed exhaust port; 25, receiving groove; 30, piston assembly; 31, variable volume chamber; Guide hole; 32, piston; 321, slip hole; 33, piston sleeve; 332, first thrust surface; 333, piston sleeve shaft; 34, partition; 35, oil hole; 40, exhaust valve assembly 41, exhaust valve plate; 42, valve plate baffle; 43, first fastener; 50, upper flange; 60, lower flange; 61, support plate; 611, second thrust surface; a second fastener; 80, a third fastener; 82, a fourth fastener; 90, a dispenser component; 91, a housing assembly; 92, a motor assembly; 93, a pump body assembly; Components; 95, lower cover and mounting plate.

detailed description

It should be noted that the embodiments in the present application and the features in the embodiments may be combined with each other without conflict. The invention will be described in detail below with reference to the drawings in conjunction with the embodiments.

It should be noted that the following detailed description is illustrative and is intended to provide a further description of the application. All technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs, unless otherwise indicated.

In the present invention, the orientation words such as "left and right" are generally referred to as left and right as shown in the drawings, and the "inside and outside" are relative to the outline of each component, unless otherwise stated. The inside and outside, but the above orientation words are not intended to limit the invention.

In order to solve the problem that the compressor of the prior art has motion instability, large vibration, and a clearance volume, the present invention provides a compressor and a heat exchange device, wherein the heat exchange device includes the following compressor. In addition, a method of operating the compressor is also provided.

As shown in FIG. 2 to FIG. 23, the compressor includes an upper flange 50, a lower flange 60, at least two cylinders 20, a rotating shaft assembly and a piston assembly 30, and at least two cylinders 20 are sandwiched between the upper flange 50 and the lower method. Between the waves 60, any two adjacent cylinders 20 operate independently of each other, the shaft assembly sequentially passes through the upper flange 50, the cylinder 20 and the lower flange 60, and the shaft assembly includes and each of the at least two cylinders 20 The spindle shaft 10 is disposed correspondingly, the axis of the sub-rotating shaft 10 is eccentrically disposed with the axis of the cylinder 20 corresponding to the sub-rotating shaft 10, and the eccentric distance is fixed, and the piston assembly 30 has a variable volume chamber corresponding to each cylinder 20 in one-to-one correspondence. 31. The piston assembly 30 is pivotally disposed within the cylinder 20 and at least one sub-rotor 10 is drivingly coupled to the piston assembly 30 to vary the volume of the variable volume chamber 31. The upper flange 50 is fixed to the cylinder 20 on the side close to the upper flange 50 by the second fastener 70, and the lower flange 60 is fixed to the cylinder 20 on the side close to the lower flange 60 by the third fastener 80.

Preferably, the second fastener 70 and/or the third fastener 80 are screws or bolts.

Preferably, the upper flange 50 is provided with a first pump body screw hole through which the second fastener 70 is inserted. The lower flange 60 is provided with four second pump body screw holes for the third fastener 80 to pass through.

It should be noted that the center of the first pump body screw hole on the upper flange 50 and the center of the upper flange 50 have a certain eccentricity e. This eccentricity determines the displacement of the cylinder 20 near the upper flange 50. When the cylinder 20 rotates one revolution, the gas displacement is V = 2 * 2e * S, where S is the cross-sectional area of the piston body structure.

Any two adjacent cylinders 20 are operated independently of each other, and the sub-axis is fixed by eccentrically setting the axis of the sub-rotary shaft 10 in the rotating shaft assembly and the axis of the cylinder 20 corresponding to the sub-rotating shaft 10 and fixing the eccentric distance. 10 and the cylinder 20 rotate around their respective axes during the movement, and the position of the center of mass is constant, thereby enabling the piston assembly 30 to rotate stably and continuously during the movement of the cylinder, thereby effectively alleviating the vibration of the compressor and ensuring variable volume. The volume change of the cavity 31 has a regularity, and the clearance volume is reduced, thereby improving the operational stability of the compressor, thereby improving the operational reliability of the heat exchange device.

It should be noted that the adjacent two cylinders 20 are disposed concentrically with each other. Preferably, the axis of the upper flange 50 is eccentric from the axis of the cylinder 20 disposed on the side close to the upper flange 50. Preferably, the axis of the lower flange 60 is eccentric from the axis of the cylinder 20 disposed on the side close to the lower flange 60. The cylinder 20 mounted in the above manner can ensure that the eccentricity of the cylinder 20 and the sub-rotary shaft 10 or the upper flange 50 is fixed, so that the piston assembly 30 has a characteristic of good motion stability.

The sub-rotary shaft 10 in the present invention is slidably coupled to the piston assembly 30, and the volume of the variable volume chamber 31 varies with the rotation of the sub-rotary shaft 10. Since the sub-rotary shaft 10 of the present invention is slidably coupled with the piston assembly 30, the movement reliability of the piston assembly 30 is ensured, and the problem of the movement of the piston assembly 30 is effectively avoided, so that the volume change of the variable volume chamber 31 has regular characteristics. .

As shown in FIGS. 2, 10 to 13, and 17 to 23, the piston assembly 30 includes a piston sleeve 33 and at least two pistons 32. The piston sleeve 33 is pivotally disposed within the cylinder 20, and the piston 32 is slidably disposed at The variable displacement chamber 31 is formed in the piston sleeve 33, and the variable volume chamber 31 is located in the sliding direction of the piston 32. Alternatively, the number of pistons 32 coincides with the number of cylinders 20.

In this particular embodiment, the piston assembly 30 is slidably engaged with the sub-rotary shaft 10, and as the sub-rotation shaft 10 rotates, the piston assembly 30 has a linear motion tendency with respect to the sub-rotation shaft 10, thereby causing the rotation to become a local linear motion. Since the piston 32 is slidably coupled with the piston sleeve 33, the movement of the piston 32 is effectively prevented from being driven by the driving of the sub-rotating shaft 10, thereby ensuring the reliability of the movement of the piston 32, the sub-rotating shaft 10 and the piston sleeve 33, thereby improving the compressor. Operational stability.

In the preferred embodiment shown in FIG. 1 to FIG. 23 and FIG. 24, the cylinder 20, the sub-rotating shaft 10, and the piston 32 are each two, and one sub-rotating shaft 10 as a driving shaft extends through the upper flange 50 into the upper flange. The cylinder 20 on one side of the 50 is movably connected to the piston 32 in the cylinder 20; the other sub-rotor 10 as a passive shaft extends through the lower flange 60 into the cylinder 20 near the side of the lower flange 60, and The piston 32 within the cylinder 20 is movably coupled. Since the cross slide mechanism is formed between the piston assembly 30, the cylinder 20 and the sub-rotation shaft 10, the movement of the piston assembly 30 and the cylinder 20 is stabilized and continuous, and the volume change of the variable volume chamber 31 is ensured to be regular, thereby ensuring the compressor. Operational stability, which in turn improves the operational reliability of the heat exchange equipment.

The drive shaft is driven to rotate by the motor, and the driven shaft is driven indirectly by the drive shaft.

The piston 32 of the present invention has a sliding hole 321 disposed through the axial direction of the sub-rotating shaft 10, and the sub-rotating shaft 10 passes through the sliding hole 321, and the piston 32 engaged with the driving shaft rotates with the driving shaft under the driving of the driving shaft. At the same time, the piston 32 is reciprocally slid in the axial direction perpendicular to the driving shaft; the piston 32 engaged with the passive shaft rotates with the piston sleeve 33 under the driving of the piston sleeve 33 and drives the driven shaft to rotate, and the piston cooperates with the passive shaft. 32 reciprocally slides within the piston sleeve 33 in an axial direction perpendicular to the passive shaft. Since the piston 32 is linearly moved relative to the sub-rotating shaft 10 instead of rotating and reciprocating, the eccentric mass is effectively reduced, and the lateral forces received by the sub-rotary shaft 10 and the piston 32 are reduced, thereby reducing the wear of the piston 32 and improving the piston. 32 sealing performance.

For the above-mentioned passive shaft, that is, the sub-rotary shaft 10 disposed in the cylinder 20 on the side close to the lower flange 60, the piston sleeve 33 rotates and drives the piston 32 to rotate, and the piston 32 disposed on the side close to the lower flange 60 is provided. The piston sleeve 33 is slid to change the volume of the corresponding variable volume chamber 31, while the sub-rotary shaft 10 near the lower flange 60 side is rotated by the driving of the piston 32, thereby causing the piston sleeve 33 and the sub-rotating shaft 10 The bending deformation and the torsional deformation are respectively taken down, the overall deformation of the individual parts is reduced, and the structural strength requirement for the sub-rotating shaft 10 is lowered.

Preferably, the sliding hole 321 is a long hole or a waist hole.

The piston 32 in the present invention has a cylindrical shape. Preferably, the piston 32 is cylindrical or non-cylindrical.

As shown in FIGS. 10 and 11, the piston 32 has a pair of arcuate surfaces symmetrically disposed along the median plane of the piston 32, the arcuate surface being adaptively fitted to the inner surface of the cylinder 20, and the curvature of the curved surface of the curved surface Two times the radius is equal to the inner diameter of the cylinder 20. In this way, a zero clearance volume can be achieved during the exhaust process. It should be noted that when the piston 32 is placed in the piston sleeve 33, the vertical plane of the piston 32 is the axial plane of the piston sleeve 33.

The main structure of the piston sleeve 33 in the present invention is a hollow cylinder having a certain roughness requirement.

In the preferred embodiment shown in FIG. 12 and FIG. 13 , the piston sleeve 33 has a guiding hole 311 extending through the radial direction of the piston sleeve 33 . The guiding hole 311 is at least two, and each guiding hole 311 is correspondingly disposed. A piston 32, the piston 32 is slidably disposed in the guide hole 311 to reciprocate linearly. Since the piston 32 is slidably disposed in the guiding hole 311, when the piston 32 moves left and right in the guiding hole 311, the volume of the variable volume chamber 31 can be continuously changed, thereby ensuring the suction and exhaust stability of the compressor.

In order to prevent the piston 32 from rotating within the piston sleeve 33, the orthographic projection of the pilot hole 311 at the lower flange 60 has a pair of parallel straight segments, and a pair of parallel straight segments are a pair of parallel inner wall faces of the piston sleeve 33. The projection is formed, and the piston 32 has an outer surface that is adapted to the shape of the pair of parallel inner wall faces of the guide hole 311 and that is slip-fitted. The piston 32 and the piston sleeve 33, which are configured as described above, enable the piston 32 to smoothly slide in the piston sleeve 33 and maintain a sealing effect.

Preferably, the orthographic projection of the pilot hole 311 at the lower flange 60 has a pair of arcuate segments joined to a pair of parallel straight segments to form an irregular cross-sectional shape.

As shown in FIG. 2, the outer peripheral surface of the piston sleeve 33 is adapted to the shape of the inner wall surface of the cylinder 20. Therefore, the piston sleeve 33 and the cylinder 20, the pilot hole 311 and the piston 32 are sealed with a large face, and the whole machine seal is a large face seal, which is beneficial to reduce leakage.

As shown in FIG. 5, the first thrust surface 332 of the piston sleeve 33 facing the lower flange 60 side is in contact with the surface of the lower flange 60. Thereby, the piston sleeve 33 and the lower flange 60 are reliably positioned.

As shown in FIG. 12 and FIG. 13, a partition plate 34 is formed between the adjacent two guide holes 311 in the piston sleeve 33, and the oil passage hole 35 for communicating the adjacent two guide holes 311 is formed in the partition plate 34. The oil passage hole 35 is for ensuring that the sub-rotary shaft 10 on both sides of the partition plate 34 can smoothly obtain lubrication of the lubricating oil.

Preferably, the axis of the oil passage 35 is parallel to the axis of the sub-rotation shaft 10.

Preferably, the axes of each of the at least two guiding holes 311 are parallel.

As shown in FIGS. 6 to 9, the sub-rotation shaft 10 has a slip section 11 that is slidably engaged with the piston assembly 30, the slip section 11 is located at one end of the sub-rotary shaft 10 near the cylinder 20, and the slip section 11 has a slip fit surface. 111. Since the sub-rotating shaft 10 is slidably engaged with the sliding hole 321 of the piston 32 through the sliding mating surface 111, the motion reliability of the two is ensured, and the two are effectively prevented from being stuck.

In particular, the sub-rotating shaft 10 disposed on the side of the lower flange 60, the sliding mating surface 111 of the sub-rotating shaft 10 cooperates with the hole wall surface of the sliding hole 321 of the corresponding piston 32, so that the piston 32 drives the sub-rotating shaft 10 Turn.

Preferably, the slip section 11 has two symmetrical arrangement of slip fit faces 111. Since the sliding mating faces 111 are symmetrically disposed, the forces of the two slip mating faces 111 are more uniform, and the reliability of the movement of the sub-rotating shaft 10 and the piston 32 is ensured.

As shown in FIGS. 6 to 9, the sub-rotation shaft 10 has a slip section 11 that is slidably engaged with the piston assembly 30, the slip section 11 is located at one end of the sub-rotary shaft 10 near the cylinder 20, and the slip section 11 has two symmetrical settings. The slip fit surface 111.

Preferably, the slip mating surface 111 is parallel to the axial plane of the sub-rotating shaft 10, and the slip mating surface 111 is slidably engaged with the inner wall surface of the sliding hole 321 of the piston 32 in the axial direction perpendicular to the sub-rotating shaft 10.

The sub-rotary shaft 10 in the present invention has a lubricating oil passage 13, and at least a part of the lubricating oil passage 13 is an internal oil passage of the sub-rotating shaft 10. Due to at least a part of the internal oil passage of the lubricating oil passage 13, the lubricating oil is effectively prevented from leaking out a large amount, and the flow reliability of the lubricating oil is improved.

As shown in FIGS. 6 to 9, the lubricating oil passage 13 at the slip fitting surface 111 is an outer oil passage. Since the lubricating oil passage 13 at the slip fitting surface 111 is an external oil passage, the lubricating oil can be directly supplied to the sliding mating surface 111 and the piston 32, thereby effectively avoiding excessive friction and wear of the two, thereby improving the two. The smoothness of the movement.

The sub-rotary shaft 10 in the present invention has an oil passage hole 14, and the inner oil passage communicates with the outer oil passage through the oil passage hole 14. Since the oil passage hole 14 is provided, the inner and outer oil passages can be smoothly communicated, and oil can be injected into the lubricating oil passage 13 through the oil passage hole 14, thereby ensuring the oil filling convenience of the lubricating oil passage 13.

The compressor of the present invention further includes a support plate 61 disposed on an end surface of the lower flange 60 away from the cylinder 20 side, and the support plate 61 and the lower flange 60 are disposed concentrically to support the shaft assembly, the sub-shaft 10 is supported on the support plate 61 through a through hole in the lower flange 60, and the support plate 61 has a second thrust surface 611 for supporting the sub-rotation shaft 10. Since the support plate 61 is provided for supporting the sub-rotary shaft 10, the connection reliability between the components is improved.

Since the support plate 61 is disposed on the side of the lower flange 60, the support plate 61 is mainly used to support the sub-rotation shaft 10 disposed on the side close to the lower flange 60 to ensure the mounting reliability thereof.

As shown in Figures 4a and 4b, the support plate 61 is coupled to the lower flange 60 by a fourth fastener 82.

Preferably, the fourth fastener 82 is a bolt or a screw.

Preferably, the lower flange 60 is provided with three support plate screw holes for the fourth fastener 82 to pass through. The circle formed by the center of the four pump body screw holes on the lower flange 60 is eccentric to the center of mass of the lower flange 60, and the amount of eccentricity is e, which determines the assembly of the cylinder 20 near the side of the lower flange 60. The eccentric amount is rotated one time in the piston sleeve 33, and the gas displacement V=2*2e*S, where S is the cross-sectional area of the piston main body structure; the center of the screw hole of the support plate coincides with the axial center of the lower flange 60, and The four fasteners 82 cooperate with the fixed support plate 61.

As shown in FIG. 2, the support plate 61 has a cylindrical structure and is evenly distributed with three screw holes. The end face of the support plate 61 has a certain roughness requirement, and is fitted to the bottom surface of the sub-rotary shaft 10 on the side close to the lower flange 60.

As shown in FIG. 1, the compressor includes a dispenser member 90, a housing assembly 91, a motor assembly 92, a pump body assembly 93, an upper cover assembly 94, and a lower cover and mounting plate 95, wherein the dispenser member 90 is disposed On the outside of the housing assembly 91, the upper cover assembly 94 is fitted to the upper end of the housing assembly 91, the lower cover and the mounting plate 95 are fitted to the lower end of the housing assembly 91, and the motor assembly 92 and the pump body assembly 93 are both located at the housing assembly 91. The interior of the pump assembly 93 is disposed. The pump body assembly 93 of the compressor includes the upper flange 50, the lower flange 60, the cylinder 20, the shaft assembly, and the piston assembly 30 described above.

Preferably, the above components are joined by welding, hot jacketing, or cold pressing.

The assembly process of the entire pump body assembly 93 is as follows: the piston 32 is mounted in the guide hole 311, while the cylinder 20 is coaxially mounted with the piston sleeve 33, and the lower flange 60 is fixed to the cylinder 20, and the slip fit surface 111 of the sub-rotor shaft 10 is A pair of parallel surfaces of the sliding holes 321 of the piston 32 are fitted together, and the upper flange 50 fixes the drive shaft while the upper flange 50 is fixed to the cylinder 20 by screws. Thereby the assembly of the pump body assembly 93 is completed, as shown in FIG.

Preferably, the compressor of the present invention is not provided with an intake valve piece, so that the suction resistance can be effectively reduced and the compression efficiency of the compressor can be improved.

It should be noted that, in this embodiment, when one piston 32 completes one-week movement, it inhales and exhausts twice, so that the compressor has a high compression efficiency. Compared with the single-displacement single-cylinder roller compressor, since the original primary compression is divided into two compressions, the torque fluctuation of the compressor in the present invention is relatively small, and the exhaust resistance is small and effective during operation. Eliminates exhaust noise.

Specifically, as shown in FIGS. 17 to 23, the cylinder wall of each cylinder 20 in the present invention has a compression intake port 21 and a first compression exhaust port 22, which is compressed when the piston assembly 30 is in the intake position. The intake port 21 is electrically connected to the variable volume chamber 31; when the piston assembly 30 is in the exhaust position, the variable volume chamber 31 is electrically connected to the first compressed exhaust port 22.

Preferably, the inner wall surface of the cylinder wall has a compressed intake buffer groove 23, and the compressed intake buffer groove 23 communicates with the compressed intake port 21 (please refer to FIGS. 17 to 23). Since the compressed air intake buffer tank 23 is provided, a large amount of gas is stored therein, so that the variable volume chamber 31 can be fully inhaled, so that the compressor can sufficiently inhale, and when the air intake is insufficient, The storage gas can be supplied to the variable volume chamber 31 in time to ensure the compression efficiency of the compressor.

Specifically, the compressed intake buffer groove 23 has an arc segment in the radial plane of the cylinder 20, and the compressed intake buffer groove 23 extends from the compressed intake port 21 toward the side of the first compression exhaust port 22, And the direction in which the compressed intake buffer groove 23 extends is in the same direction as the rotational direction of the piston assembly 30.

The cylinder wall of each cylinder 20 in the present invention has a second compressed exhaust port 24, and the second compressed exhaust port 24 is located between the compressed intake port 21 and the first compressed exhaust port 22, and is rotated at the piston assembly 30. During the process, part of the gas in the piston assembly 30 is first discharged through the second compressed exhaust port 24 and then discharged from the first compressed exhaust port 22. Since only two exhaust passages are provided, one is exhausted through the first compressed exhaust port 22, and the other is exhausted through the second compressed exhaust port 24, thereby reducing gas leakage and increasing the sealing area of the cylinder 20. .

Preferably, the compressor further includes an exhaust valve assembly 40 disposed at the second compressed exhaust port 24. Since the exhaust valve assembly 40 is provided at the second compression exhaust port 24, a large amount of gas leakage in the variable volume chamber 31 is effectively prevented, and the compression efficiency of the variable volume chamber 31 is ensured.

In the preferred embodiment shown in FIG. 5, the outer wall of the cylinder wall is provided with a receiving groove 25, and the second compressed exhaust port 24 penetrates the groove bottom of the receiving groove 25, and the exhaust valve assembly 40 is disposed in the receiving groove 25. Since the accommodating groove 25 for accommodating the vent valve assembly 40 is provided, the space occupied by the vent valve assembly 40 is reduced, and the components are properly disposed, thereby increasing the space utilization of the cylinder 20.

Specifically, the exhaust valve assembly 40 includes an exhaust valve plate 41 and a valve flapper 42 disposed in the receiving groove 25 and blocking the second compressed exhaust port 24, and the valve flapper 42 is stacked On the exhaust valve piece 41. Since the valve flapper 42 is provided, the exhaust valve flap 41 is effectively prevented from being excessively opened, and the exhaust performance of the cylinder 20 is ensured.

Preferably, the exhaust valve flap 41 and the valve flapper 42 are connected by a first fastener 43. Further, the first fastener 43 is a screw.

It should be noted that the exhaust valve assembly 40 of the present invention can separate the variable volume chamber 31 from the external space of the pump body assembly 93, and is a back pressure exhaust gas: that is, when the variable volume chamber 31 and the second compressed exhaust port After 24 communication, when the pressure of the variable volume chamber 31 is greater than the external space pressure (exhaust pressure), the exhaust valve piece 41 is opened to start the exhaust; if the pressure of the variable volume chamber 31 is still lower than the exhaust pressure after the communication, At this time, the exhaust valve piece 41 does not operate. At this time, the compressor continues to operate and compress until the variable volume chamber 31 communicates with the first compressed exhaust port 22, and the gas in the variable volume chamber 31 is pressed into the external space to complete the exhaust process. The exhaust mode of the first compression exhaust port 22 is a forced exhaust mode.

The following is a detailed description of the operation of the compressor, taking counterclockwise rotation as an example:

As shown in Fig. 24, the compressor of the present invention is set using the principle of a cross slider mechanism. The axis O _{1 of the} sub-rotating shaft 10 is eccentrically disposed with the axis O _{2 of the} cylinder 20 , and the eccentricity of the two is fixed to e, and the two are respectively rotated about the respective axes. The piston 32 corresponds to a slider in the cross slider mechanism, the distance from the axial center of the piston sleeve 33 to the axial center of the piston 32 and the distance from the axial center of the sub-rotating shaft 10 to the axial center of the piston 32 correspond to two connecting rods, respectively. ₁ , l ₂ , this constitutes the main structure of the principle of the cross slider.

As shown in Fig. 24, when the compressor of the above configuration is operated, the sub-rotating shaft 10 is rotated about the axis O _{1 of the} sub-rotary shaft 10; the cylinder 20 is rotated about the axis O _{2 of the} cylinder 20, and the axis and the cylinder of the sub-rotating shaft 10 are The axial center of 20 is eccentrically disposed and the eccentric distance is fixed; the piston 32 of the piston assembly rotates with the sub-rotating shaft 10 under the driving of the sub-rotating shaft 10 while simultaneously reciprocatingly sliding in the piston sleeve 33 of the piston assembly in the direction perpendicular to the axis of the sub-rotating shaft 10.

The compressor operated by the above method constitutes a cross slide mechanism, and the operation method adopts the principle of a cross slide mechanism, wherein the piston 32 serves as a slider, and the slip fit surface 111 of the sub-rotor shaft 10 serves as the first link l ₁ , The guide hole 311 of the piston sleeve 33 serves as a second link ₁₂ (refer to Fig. 24).

Specifically, the axis O ₁ of the sub-rotating shaft 10 corresponds to the center of rotation of the first link ₁₁ , the axis O _{2 of the} cylinder 20 corresponds to the center of rotation of the second link ₁₂ ; and the slip fit of the sub-shaft 10 The surface 111 corresponds to the first link l ₁ , the guide hole 311 of the piston sleeve 33 corresponds to the second link l ₂ , and the piston 32 corresponds to the slider. The guiding hole 311 and the sliding mating surface 111 are perpendicular to each other; the piston 32 can only reciprocate relative to the guiding hole 311, and the piston 32 can only reciprocate relative to the sliding mating surface 111. The piston 32 can be simplified to find the centroid, which running track is a circular motion, the circular cylinder axis O is 20 in the shaft ₂ and the sub line connecting the axis O 10 is _a circular diameter.

When the second link ₁₂ moves in a circular motion, the slider can reciprocate along the second link ₁₂ ; at the same time, the slider can reciprocate along the first link ₁₁ . The first link and the second link l ₁ l ₂ remain vertically, so that the slider along the first link l ₁ reciprocates along the direction perpendicular to the second slider link l ₂ reciprocating direction. The relative motion relationship between the first link l ₁ and the second link l ₂ and the piston 32 forms the principle of the cross slider mechanism.

Under the motion method, the slider performs a circular motion whose angular velocity is equal to the rotational speed of the first link ₁₁ and the second link ₁₂ . The slider runs in a circle. The circle has a diameter centered on the center of rotation of the first link l _{1 and} the center of rotation of the second link l ₂ . In the embodiment shown in Figure 3, the two cylinders 20 are arranged 180 degrees apart. The two pistons 32 form four variable volume chambers 31 during the reciprocating motion. And the two dispenser parts 90 corresponding to the two cylinders 20 are arranged at an interval of 180 degrees. Of course, it is also conceivable to arrange the two dispenser parts 90 on the same side, so that the two cylinders 20 should also be arranged without any misalignment, completely overlapping.

As shown in FIG. 16 and FIG. 24, the axis 15 of the sub-rotating shaft near the lower flange side and the piston sleeve axis 333 are separated by an eccentric distance e, and the piston centroid trajectory line is circular.

Specifically, the motor assembly 92 drives the sub-rotating shaft 10 near the upper flange 50 to rotate, and the sliding mating surface 111 of the sub-rotating shaft 10 drives the piston 32 on the side close to the upper flange 50, and the piston 32 drives the piston sleeve 33 to rotate. In turn, the piston 32 near the side of the lower flange 60 is rotated, and the sub-rotary shaft 10 near the side of the lower flange 60 is caused to rotate. In the entire moving part, the piston sleeve 33 only moves in a circular motion, and the piston 32 reciprocates on the one hand with respect to the sub-rotation shaft 10 while reciprocating relative to the guide hole 311 of the piston sleeve 33, and the two reciprocating motions are perpendicular to each other and simultaneously The reciprocating motion in both directions constitutes a motion of the cross slider mechanism. The combined motion of the cross-type slider mechanism reciprocates the piston 32 relative to the piston sleeve 33, which reciprocates the cavity formed by the piston sleeve 33, the cylinder 20 and the piston 32 periodically. The piston 32 is circumferentially moved relative to the cylinder 20, and the circular motion causes the variable displacement chamber 31 formed by the piston sleeve 33, the cylinder 20 and the piston 32 to periodically communicate with the compressed intake port 21 and the exhaust port. Under the combined action of the above two relative movements, the compressor can complete the process of inhaling, compressing and exhausting. During the reciprocating motion, the centroid trajectory of the piston 32 is circular, the diameter of the circle is equal to the eccentricity e, and the center of the circle is at the midpoint of the center of the sub-rotating shaft 10 and the center of the piston sleeve 33.

As shown in FIG. 17 to FIG. 23 and FIG. 24, taking a variable volume chamber 31 as an example, when the variable volume chamber 31 is in communication with the compressed air inlet 21, air intake is started (please refer to FIG. 17 and FIG. 18); 33 continues to drive the piston 32 and the sub-rotating shaft 10 to rotate clockwise. When the variable volume chamber 31 is separated from the compressed air inlet 21, the entire inhalation ends, at which time the variable volume chamber 31 is completely sealed and begins to compress (please refer to FIG. 18); Rotating, the gas is continuously compressed, and when the variable volume chamber 31 is in communication with the second compressed exhaust port 24, the exhaust gas is started (please refer to FIG. 19); the rotation is continued, and the air is continuously compressed while continuously venting until the variable volume chamber 31 is completely separated. The first compressed exhaust port 22 completes the entire inhalation, compression, and exhaust process (please refer to FIG. 21 to FIG. 23); then the variable volume chamber 31 is rotated by a certain angle and then the compressed intake port 21 is connected again. The total displacement of the compressor is V = 2 * 2 * (2e * S).

In addition, the compressor of the present invention has the advantages of zero clearance volume and high volumetric efficiency, and at the same time, it can effectively expand the displacement of the compressor and reduce the torque fluctuation of the compressor.

It is to be noted that the terminology used herein is for the purpose of describing particular embodiments, and is not intended to limit the exemplary embodiments. As used herein, the singular " " " " " " There are features, steps, operations, devices, components, and/or combinations thereof.

It should be noted that the terms "first", "second" and the like in the specification and claims of the present application and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or order. It is to be understood that the data so used may be interchanged where appropriate, so that the embodiments of the present application described herein can be implemented in a sequence other than those illustrated or described herein.

The above description is only the preferred embodiment of the present invention, and is not intended to limit the present invention, and various modifications and changes can be made to the present invention. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and scope of the present invention are intended to be included within the scope of the present invention.

Claims

A compressor, comprising:

Upper flange (50);

Lower flange (60);

At least two cylinders (20) interposed between the upper flange (50) and the lower flange (60), any two adjacent cylinders (20) ) work independently of each other;

a shaft assembly that sequentially passes through the upper flange (50), the cylinder (20), and the lower flange (60), the shaft assembly including the at least two cylinders (20) Each of the cylinders (20) corresponds to a sub-rotation shaft (10), and an axis of the sub-rotation shaft (10) and an axis of the cylinder (20) corresponding to the sub-rotation shaft (10) The heart is eccentrically set and the eccentric distance is fixed;

a piston assembly (30) having a variable volume chamber (31) in one-to-one correspondence with each of the cylinders (20), the piston assembly (30) being pivotally disposed at the cylinder (20), and at least one of the sub-rotating shafts (10) is drivingly coupled to the piston assembly (30) to change the volume of the variable volume chamber (31).
The compressor of claim 1 wherein said piston assembly (30) comprises:

a piston sleeve (33), the piston sleeve (33) being pivotally disposed within the cylinder (20);

At least two pistons (32) slidably disposed within the piston sleeve (33) to form the variable volume chamber (31), and the variable volume chamber (31) is located at the piston ( 32) in the sliding direction.
The compressor according to claim 2, wherein said cylinder (20), said sub-rotating shaft (10), and said piston (32) are each two,

One of the sub-rotating shafts (10) is a drive shaft that extends through the upper flange (50) into the cylinder (20) near one side of the upper flange (50), and with the cylinder The piston (32) in (20) is movably connected;

The other sub-rotating shaft (10) is a passive shaft that extends through the lower flange (60) into the cylinder (20) near one side of the lower flange (60), and The piston (32) in the cylinder (20) is movably coupled.
The compressor according to claim 3, wherein said drive shaft is driven to rotate by a motor, and said driven shaft is indirectly driven to rotate by said drive shaft.
The compressor according to claim 4, wherein said piston (32) has a sliding hole (321) disposed in an axial direction of said sub-rotating shaft (10), said sub-rotating shaft (10) Passing through the sliding hole (321),

The piston (32) engaged with the driving shaft rotates with the driving shaft under the driving of the driving shaft and simultaneously reciprocates in the piston sleeve (33) in an axial direction perpendicular to the driving shaft ;

The piston (32) cooperating with the passive shaft rotates with the piston sleeve (33) under the driving of the piston sleeve (33) and drives the passive shaft to rotate while being engaged with the passive shaft The piston (32) reciprocally slides within the piston sleeve (33) in an axial direction perpendicular to the driven shaft.
The compressor according to claim 5, characterized in that the sliding hole (321) is a long hole or a waist hole.
The compressor according to claim 2, wherein said piston (32) has a pair of arcuate surfaces symmetrically disposed along a center plane of said piston (32), said curved surface being said The inner surface of the cylinder (20) is adaptively fitted, and the radius of curvature of the curved surface of the curved surface is equal to twice the inner diameter of the cylinder (20).
The compressor according to claim 2, wherein said piston (32) has a cylindrical shape.
The compressor according to claim 2, wherein the piston sleeve (33) has a guide hole (311) disposed in a radial direction of the piston sleeve (33), the guide hole (311) For at least two, each of the guiding holes (311) is correspondingly provided with one piston (32), and the piston (32) is slidably disposed in the guiding hole (311) to reciprocate linearly.
The compressor according to claim 9, wherein an axis of each of said guide holes (311) is parallel.
The compressor according to claim 9, wherein a partition (34) is formed between adjacent ones of said pilot holes (311) in said piston sleeve (33), said partition (34) The upper opening is provided with an oil passage hole (35) for connecting two adjacent guide holes (311).
The compressor according to claim 11, characterized in that the axis of the oil passage (35) is parallel to the axis of the sub-rotating shaft (10).
The compressor according to claim 9, wherein the orthographic projection of said guide hole (311) at said lower flange (60) has a pair of parallel straight line segments, said pair being parallel a straight line segment is formed by projecting a pair of parallel inner wall faces of the piston sleeve (33), the piston (32) having an inner wall surface shape parallel to the pair of the guide holes (311) And slip fit the outer profile.
The compressor according to claim 2, wherein a first thrust surface (332) and a lower flange (60) of the piston sleeve (33) facing the lower flange (60) side are provided. ) surface contact.
The compressor according to claim 5, wherein said sub-rotating shaft (10) has a slip section (11) that is slidably engaged with said piston assembly (30), said slip section (11) being located An end of the spindle (10) adjacent to the cylinder (20), and the slip section (11) has a slip fit surface (111).
The compressor according to claim 15, characterized in that the slip mating faces (111) are symmetrically disposed on both sides of the slip section (11).
The compressor according to claim 16, wherein said slip fitting surface (111) is parallel to an axial plane of said sub-rotating shaft (10), said slip mating surface (111) is said An inner wall surface of the sliding hole (321) of the piston (32) is slidably fitted in an axial direction perpendicular to the sub-rotation shaft (10).
The compressor according to claim 15, wherein said sub-rotating shaft (10) has a lubricating oil passage (13) including an inner portion disposed inside said sub-rotating shaft (10) An oil passage and an outer oil passage disposed at the slip fitting surface (111) and an oil passage hole (14) communicating the inner oil passage and the outer oil passage.
The compressor according to claim 1, characterized in that two adjacent said cylinders (20) are arranged concentrically with each other.
The compressor according to claim 19, wherein an axis of said upper flange (50) is eccentrically disposed with respect to an axis of said cylinder (20) disposed on a side close to said upper flange (50) .
The compressor according to claim 20, wherein an axis of said lower flange (60) is eccentrically disposed with respect to an axis of said cylinder (20) disposed on a side close to said lower flange (60) .
The compressor according to any one of claims 1 to 21, wherein the compressor further comprises a support plate (61), the support plate (61) being disposed at the lower flange (60) Far from the end face of one side of the cylinder (20), and the support plate (61) is disposed concentrically with the lower flange (60) to support the rotating shaft assembly, the support plate (61) has a function And a second thrust surface (611) for supporting the shaft assembly.
The compressor according to claim 1, wherein a cylinder wall of each of said cylinders (20) has a compressed intake port (21) and a first compressed exhaust port (22),

The compressed air inlet (21) is electrically connected to the variable volume chamber (31) when the piston assembly (30) is in an intake position;

The variable volume chamber (31) is in communication with the first compressed exhaust port (22) when the piston assembly (30) is in an exhaust position.
The compressor according to claim 23, wherein an inner wall surface of said cylinder wall has a compressed intake buffer tank (23), said compressed intake buffer tank (23) and said compressed air inlet (21) ) Connected.
The compressor according to claim 24, wherein said compressed intake buffer tank (23) has an arc segment in a radial plane of said cylinder (20), and said compressed intake buffer tank ( 23) extending from the compressed intake port (21) to a side of the first compressed exhaust port (22).
The compressor according to claim 23, wherein a cylinder wall of each of said cylinders (20) has a second compressed exhaust port (24), said second compressed exhaust port (24) being located Compressing the intake port (21) between the first compression exhaust port (22), and during the rotation of the piston assembly (30), a portion of the gas in the piston assembly (30) passes first After the pressure is released from the second compressed exhaust port (24), all of the first compressed exhaust ports (22) are discharged.
The compressor according to claim 26, wherein said compressor further comprises an exhaust valve assembly (40), said exhaust valve assembly (40) being disposed at said second compressed exhaust port (24) At the office.
The compressor according to claim 27, wherein the outer wall of the cylinder wall is provided with a receiving groove (25), and the second compressed exhaust port (24) penetrates the groove of the receiving groove (25) The exhaust valve assembly (40) is disposed in the receiving groove (25).
The compressor according to claim 28, wherein said exhaust valve assembly (40) comprises:

An exhaust valve piece (41), the exhaust valve piece (41) is disposed in the receiving groove (25) and blocks the second pressure Shrinking port (24);

A valve flapper (42) is stacked on the exhaust valve flap (41).
A heat exchange apparatus comprising a compressor, characterized in that the compressor is the compressor according to any one of claims 1 to 29.
A method for operating a compressor, comprising:

The sub-rotating shaft (10) rotates about the axis O 1 of the sub-rotating shaft (10);

The cylinder (20) rotates around the axis O 2 of the cylinder (20), and the axis of the sub-rotating shaft (10) is eccentrically disposed with the axis of the cylinder (20) and the eccentric distance is fixed;

a piston (32) of the piston assembly (30) is rotated by the sub-rotary shaft (10) with the sub-rotation shaft (10) while being in the axial direction perpendicular to the sub-rotation shaft (10) at the piston assembly (30) The piston sleeve (33) slides back and forth.
The operating method according to claim 31, wherein said operating method adopts a principle of a cross slider mechanism, wherein said piston (32) acts as a slider, and a slip fit surface of said sub-rotating shaft (10) 111) As the first link l 1 , the pilot hole (311) of the piston sleeve (33) serves as the second link l 2 .