WO2017024864A1

WO2017024864A1 - Fluid machinery, heat exchange device, and method for operating fluid machinery

Info

Publication number: WO2017024864A1
Application number: PCT/CN2016/084324
Authority: WO
Inventors: 徐嘉; 杜忠诚; 任丽萍; 杨森; 孔令超; 张荣婷; 梁社兵; 史正良; 张金圈
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: CN106704183A; CN106704183B

Abstract

Disclosed are a fluid machinery, a heat exchange device, and a method for operating a fluid machinery. The fluid machinery comprises: an upper flange (50); a lower flange (60); a cylinder (20), the cylinder (20) being clamped between the upper flange (50) and the lower flange (60); a rotary shaft (10), an axis of the rotary shaft (10) and an axis of the cylinder (20) being eccentrically arranged with eccentric distance being fixed, and the rotary shaft (10) passing through the upper flange (50) and the cylinder (20) in sequence; and a piston assembly (30), the piston assembly (30) being provided with a variable volume cavity (31). The piston assembly (30) is pivotally arranged in the cylinder (20), and the rotary shaft (10) is connected in a driving manner to the piston assembly (30) to change the volume of the variable volume cavity (31). Since the eccentric distance between the rotary shaft (10) and the cylinder (20) is fixed, the rotary shaft (10) and the cylinder (20) rotate around the respective axis during movement, and the position of the centre of mass is unchanged so as to enable the piston assembly (30) to rotate stably and continuously when the piston assembly moves in the cylinder (20), thereby effectively relieving the vibration of the fluid machinery, guaranteeing that the volume of the variable volume cavity (31) is changed regularly, reducing a clearance volume so as to improve the stability of the operation of the fluid machinery, and accordingly improving the working reliability of the heat exchange device.

Description

Fluid machinery, heat exchange equipment, and fluid machine operation methods

Technical field

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

Background technique

Fluid machinery in the prior art includes a compressor, an expander, and the like. Take the compressor as an example.

In the prior art, the position of the center of mass of the rotary shaft and the cylinder of the piston type compressor is varied during the movement. 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

The main object of the present invention is to provide a fluid machine, a heat exchange device and a fluid machine operating method to solve the problem that the fluid machine in the prior art has motion instability, large vibration, and a clearance volume.

In order to achieve the above object, according to one aspect of the present invention, a fluid machine is provided, comprising: an upper flange; a lower flange; a cylinder, the cylinder is sandwiched between the upper flange and the lower flange; and the shaft of the rotating shaft and the rotating shaft The center of the core and the cylinder are eccentrically arranged and the eccentric distance is fixed, the rotating shaft sequentially passes through the upper flange and the cylinder; the piston assembly has a variable volume chamber, the piston assembly is pivotally disposed in the cylinder, and the rotating shaft and the piston assembly are driven Connect to change the volume of the variable volume chamber.

Further, the piston assembly includes a piston sleeve that is pivotally disposed within the cylinder, a piston that is 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 piston has a sliding hole penetratingly disposed in the axial direction of the rotating shaft, and the rotating shaft passes through the sliding hole, and the piston rotates with the rotating shaft under the driving of the rotating shaft and simultaneously reciprocates in the piston sleeve in a direction perpendicular to the axis of the rotating shaft.

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

Further, the piston has a slip groove that slidably engages the shaft.

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, and the piston is slidably disposed in the guiding hole to reciprocate linearly.

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 piston sleeve has a connecting shaft extending toward one side of the lower flange, and the connecting shaft is embedded in the connecting hole of the lower flange.

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 piston sleeve has a second thrust surface for supporting the rotating shaft, and an end surface of the rotating shaft facing the lower flange side is supported at the second thrust surface.

Further, the rotating shaft comprises: a shaft body; a connecting head, the connecting head is disposed at the first end of the shaft body and connected to the piston assembly.

Further, the connector is quadrangular in a plane perpendicular to the axis of the shaft.

Further, the connector has two symmetrically disposed slip mating faces.

Further, the sliding mating surface is parallel to the axial plane of the 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 rotating shaft.

Further, the rotating shaft has a lubricating oil passage including an internal oil passage disposed inside the rotating shaft, an external oil passage disposed outside the rotating shaft, and an oil passage hole communicating the internal oil passage and the external oil passage.

Further, the slip mating face has an outer oil passage extending in the axial direction of the rotating shaft.

Further, the upper flange is disposed concentrically with the rotating shaft, and the axial center of the upper flange and the axial center of the cylinder are eccentrically disposed.

Further, the lower flange is disposed coaxially with the cylinder.

Further, the cylinder wall of the cylinder has a compressed air inlet and a compressed air outlet, and when the piston assembly is in the intake position, the compression air inlet is electrically connected to the variable volume chamber; when the piston assembly is in the exhaust position, the variable volume chamber It is electrically connected to the 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 inlet to a side where the compression port is located.

Further, the fluid machine is a compressor.

Further, the cylinder wall of the cylinder has an expansion exhaust port and a first expansion intake port, and when the piston assembly is in the intake position, the expansion exhaust port is electrically connected to the variable volume chamber; when the piston assembly is in the exhaust position, the change is made. The volume chamber is electrically connected to the first inflation inlet.

Further, the inner wall surface of the cylinder wall has an expanded exhaust buffer tank, and the expanded exhaust buffer tank communicates with the expanded exhaust port.

Further, the expanded exhaust buffer tank has an arcuate section in a radial plane of the cylinder, and the expanded exhaust buffer tank extends from the expanded exhaust port to a side of the first inflated intake port.

Further, the fluid machine is an expander.

Further, the guiding holes are at least two, and the two guiding holes are arranged at an axial interval of the rotating shaft, and the pistons are at least two, and each of the guiding holes is correspondingly provided with a piston.

According to another aspect of the present invention, there is provided a heat exchange apparatus comprising a fluid machine, the fluid machine being the fluid machine described above.

According to another aspect of the present invention, there is provided a method of operating a fluid machine comprising: rotating a shaft about an axis O _{1 of a} rotating shaft; rotating the cylinder about an axis O _{2 of the} cylinder, and an axis of the rotating shaft and an axis of the cylinder The eccentricity is set and the eccentric distance is fixed; the piston of the piston assembly rotates with the rotating shaft under the driving of the rotating shaft and simultaneously reciprocates in the piston sleeve of the piston assembly in the axial direction perpendicular to the rotating shaft.

Further, the running method adopts the principle of the cross slider mechanism, wherein the piston acts as a slider, and the sliding mating surface of the 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 .

According to the technical solution of the present invention, the cylinder is clamped between the upper flange and the lower flange, the axial center of the rotating shaft is eccentrically arranged with the axial center of the cylinder, and the eccentric distance is fixed, and the rotating shaft sequentially passes through the upper flange and the cylinder, and the piston assembly has A variable volume chamber, the piston assembly is pivotally disposed within the cylinder, and the shaft is drivingly coupled to the piston assembly to vary the volume of the variable volume chamber. Since the eccentric distance between the rotating shaft and the cylinder is fixed, the rotating shaft and the cylinder rotate 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, effectively alleviating the fluid. The mechanical vibration ensures that the volume change of the variable volume chamber has regularity and reduces the clearance volume, thereby improving the operational stability of the fluid machine and improving the operational reliability of the heat exchange equipment.

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 mounting relationship of the rotating shaft, the upper flange, the cylinder and the lower flange in the present invention;

Figure 4 is a schematic view showing the internal structure of the components of Figure 3;

Figure 5 is a schematic view showing the structure of a cylinder in the present invention;

Figure 6 is a schematic view showing the structure of a rotating shaft in the present invention;

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

Figure 8 is a view showing the working state of the piston in the present invention when it is ready to start inhaling;

Figure 9 is a view showing the working state of the piston in the present invention in the process of inhalation;

Figure 10 is a view showing the working state of the piston in the present invention when the suction is completed;

Figure 11 is a view showing the working state of the piston in the present invention at the time of gas compression;

Figure 12 is a view showing the working state of the piston in the exhausting process of the present invention;

Figure 13 is a view showing the working state of the piston in the present invention when the exhaust gas is completed;

Figure 14 is a schematic view showing the connection relationship between the piston sleeve, the piston and the rotating shaft in the present invention;

Figure 15 is a schematic view showing the movement relationship between the piston sleeve, the piston and the rotating shaft in the present invention;

Figure 16 is a view showing the structure of the upper flange in the present invention;

Figure 17 is a cross-sectional view showing the piston sleeve of the present invention;

Figure 18 is a view showing the structure of a piston in the present invention;

Figure 19 is a view showing the structure of another angle of the piston of Figure 18;

Fig. 20 is a view showing the operation of the compressor in the present invention.

Wherein, the above figures include the following reference numerals:

10, the shaft; 16, the shaft; 17, the joint; 111, the slip fit surface; 13, the lubricating oil passage; 14, the oil hole; 15, the axis of the shaft; 335, the second thrust surface; Cylinder; 21, compressed air inlet; 22, compressed exhaust port; 23, compressed intake buffer tank; 30, piston assembly; 31, variable volume chamber; 311, guiding hole; 32, piston; 321, sliding hole; 322, piston centroid trajectory line; 33, piston sleeve; 331, connecting shaft; 333, piston sleeve axis; 332, first thrust surface; 50, upper flange; 60, lower flange; 70, first fastening 80; second fastener; 90, dispenser part; 91, housing assembly; 92, motor assembly; 93, pump body assembly; 94, upper cover assembly; 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 fluid machinery in the prior art has motion instability, large vibration, and existence of a clearance volume, the present invention provides a fluid machine and a heat exchange device, wherein the heat exchange device includes the following fluid machine. In addition, a method of operating a fluid machine is also provided.

Fluid machinery mainly includes two types of compressors and expanders. Will be introduced later. Let us first introduce the general characteristics of fluid machinery.

As shown in FIG. 2 to FIG. 19, the fluid machine includes an upper flange 50, a lower flange 60, a cylinder 20, a rotating shaft 10 and a piston assembly 30, and the cylinder 20 is interposed between the upper flange 50 and the lower flange 60, and the rotating shaft 10 is eccentrically disposed with the cylinder 20 and the eccentric distance is fixed. The rotating shaft 10 sequentially passes through the upper flange 50 and the cylinder 20. The piston assembly 30 has a variable volume chamber 31, and the piston assembly 30 is pivotally disposed in the cylinder 20, and the rotating shaft 10 and The piston assembly 30 drives the connection to change the volume of the variable volume chamber 31. The upper flange 50 is fixed to the cylinder 20 by the first fastener 70, and the lower flange 60 is fixed to the cylinder 20 by the second fastener 80.

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

Since the eccentric distance of the rotating shaft 10 and the cylinder 20 is fixed, the rotating shaft 10 and the cylinder 20 are rotated about the respective axes during the movement, and the centroid position is constant, thereby enabling the piston assembly 30 to stably and continuously when moving in the cylinder 20. Rotation, effectively alleviating the vibration of the fluid machine, and ensuring that the volume change of the variable volume chamber is regular, reducing the clearance volume, thereby improving the operational stability of the fluid machine, thereby improving the operational reliability of the heat exchange equipment.

It should be noted that the upper flange 50 and the rotating shaft 10 are disposed concentrically, and the axial center of the upper flange 50 and the axial center of the cylinder 20 are eccentric.

Preferably, the lower flange 60 is disposed concentrically with the cylinder 20. The cylinder 20 mounted in the above manner can ensure that the eccentricity of the cylinder 20 and the rotating shaft 10 or the upper flange 50 is fixed, so that the piston assembly 30 has the characteristics of good motion stability.

The rotating 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 rotating shaft 10. Since the rotating 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 a regular characteristic.

As shown in FIG. 2, FIG. 8 to FIG. 19, the piston assembly 30 includes a piston sleeve 33 and a piston 32. The piston sleeve 33 is pivotally disposed in the cylinder 20, and the piston 32 is slidably disposed in the piston sleeve 33 to form a variable volume chamber. 31, and the variable volume chamber 31 is located in the sliding direction of the piston 32.

In this particular embodiment, the piston assembly 30 is slidably engaged with the rotating shaft 10, and as the rotating shaft 10 rotates, the piston assembly 30 has a linear motion tendency with respect to the rotating shaft 10, thereby causing the rotation to become a local linear motion. Due to the piston 32 and the piston The sleeve 33 is slidably connected, so that the movement of the piston 32 is effectively prevented by the rotation of the rotating shaft 10, thereby ensuring the reliability of the movement of the piston 32, the rotating shaft 10 and the piston sleeve 33, thereby improving the operational stability of the fluid machine.

It should be noted that the rotating shaft 10 of the present invention has no eccentric structure, which is advantageous for reducing the vibration of the fluid machine.

Specifically, the piston 32 slides in the piston sleeve 33 in a direction perpendicular to the axis of the rotating shaft 10 (please refer to FIG. 2, FIG. 8 to FIG. 15, FIG. 20). Since the cross slide mechanism is formed between the piston assembly 30, the cylinder 20 and the rotating 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 regular, thereby ensuring the fluid mechanical Operational stability, which in turn improves the operational reliability of the heat exchange equipment.

The piston 32 of the present invention has a sliding hole 321 disposed through the axial direction of the rotating shaft 10, and the rotating shaft 10 passes through the sliding hole 321, and the piston 32 rotates with the rotating shaft 10 under the driving of the rotating shaft 10 while being perpendicular to the rotating shaft 10. The axial direction reciprocates in the piston sleeve 33 (please refer to Figs. 8 to 13, 18 and 19). Since the piston 32 is linearly moved relative to the rotating shaft 10 instead of rotating and reciprocating, the eccentric mass is effectively reduced, and the lateral force received by the rotating shaft 10 and the piston 32 is reduced, thereby reducing the wear of the piston 32 and improving the piston 32. Sealing performance. At the same time, the operational stability and reliability of the pump body assembly 93 are ensured, and the vibration risk of the fluid machine is reduced, and the structure of the fluid machine is simplified.

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

In a preferred embodiment, not shown, the piston 32 has a slip groove that slidably engages the shaft 10. Regardless of the slip groove or the sliding hole 321 , it is only necessary to ensure that the rotating shaft 10 and the piston 32 slide relatively reliably. Preferably, the sliding groove is a linear sliding groove, and the sliding groove extends in a direction perpendicular to the axis of the rotating shaft 10.

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

As shown in FIG. 2, the piston 32 has a pair of arcuate surfaces symmetrically disposed along the median plane of the piston 32. The curved surface is adaptively fitted to the inner surface of the cylinder 20, and the radius of curvature of the curved surface is two The multiple 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.

In the preferred embodiment shown in FIG. 2 and FIG. 17, the piston sleeve 33 has a guide hole 311 which is provided in the radial direction of the piston sleeve 33. 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.

The piston sleeve 33 of the present invention has a connecting shaft 331 that projects toward the side of the lower flange 60, and the connecting shaft 331 is embedded in the connecting hole of the lower flange 60. Since the piston sleeve 33 is coaxially embedded with the lower flange 60 through the connecting shaft 331, the connection reliability of the two is ensured, thereby improving the stability of the movement of the piston sleeve 33.

In the preferred embodiment shown in FIG. 17, the first thrust surface 332 of the piston sleeve 33 facing the side of the lower flange 60 is in contact with the surface of the lower flange 60. Thereby, the piston sleeve 33 and the lower flange 60 are reliably positioned.

Specifically, the piston sleeve 33 of the present invention includes two cylinders of coaxial but different diameters, the outer diameter of the upper half is equal to the inner diameter of the cylinder 20, and the axis of the pilot hole 311 is perpendicular to the axis of the cylinder 20 and the piston 32. The shape of the guiding hole 311 is consistent with the outer shape of the piston 32. During the reciprocating motion, gas compression is achieved, and the lower end surface of the upper half has a concentric connecting shaft 331 as a first thrust surface and a lower flange 60. The end face fits to reduce the structural friction area; the lower half is a hollow cylinder, that is, a short shaft, and the axis of the short shaft is coaxial with the axis of the lower flange 60, and rotates coaxially during the movement.

As shown in FIG. 17, the piston sleeve 33 has a second thrust surface 335 for supporting the rotary shaft 10, and an end surface of the rotary shaft 10 facing the lower flange 60 side is supported at the second thrust surface 335. Thereby, the rotating shaft 10 is supported in the piston sleeve 33.

The rotating shaft 10 in the present invention includes a shaft body 16 and a joint head 17, and the joint head 17 is disposed at a first end of the shaft body 16 and connected to the piston assembly 30. Due to the provision of the connector 17, the assembly and movement reliability of the connector 17 and the piston 32 of the piston assembly 30 are ensured.

Preferably, the axle body 16 has a certain roughness to improve the robustness of the connection to the motor assembly 92.

As shown in Figures 6 and 7, the connector 17 has two symmetrically disposed slip mating faces 111. Since the slip mating faces 111 are symmetrically disposed, the forces of the two slip mating faces 111 are more uniform, which ensures the reliability of the movement of the rotating shaft 10 and the piston 32.

As shown in FIGS. 6 and 7, the slip fitting surface 111 is parallel to the axial plane of the rotating shaft 10, and the sliding mating surface 111 and the inner wall surface of the sliding hole 321 of the piston 32 slide in the direction perpendicular to the axis of the rotating shaft 10. Cooperate.

In a preferred embodiment, not shown, the connector 17 is quadrangular in a plane perpendicular to the axis of the shaft 16. Since the connecting head 17 has a quadrangular shape in a plane perpendicular to the axis of the shaft body 16, when the sliding hole 321 of the piston 32 is engaged, the problem that the rotating shaft 10 and the piston 32 can be prevented from rotating relative to each other can be prevented, and the relative movement of the two can be ensured. Reliability.

In order to ensure the lubrication reliability of the rotating shaft 10 and the piston assembly 30, the rotating shaft 10 has a lubricating oil passage 13 which penetrates the shaft body 16 and the joint head 17.

Preferably, at least a portion of the lubricating oil passage 13 is an internal oil passage of the 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 Fig. 6, the lubricating oil passage 13 at the joint head 17 is an outer oil passage. Of course, in order to enable the lubricating oil to reach the piston 32 smoothly, the lubricating oil passage 13 at the joint head 17 is disposed as an external oil passage, so that the lubricating oil can be adhered to the surface of the sliding hole 321 of the piston 32, thereby ensuring the rotating shaft 10 Lubricity reliability with the piston 32.

The shaft body 16 and/or the joint head 17 of the present invention has an oil passage hole 14 communicating with the lubricating oil passage 13 (please refer to Figs. 6 and 7). Since the oil passage hole 14 is provided, the inner oil passage can be easily filled with oil through the oil passage hole 14, thereby ensuring lubrication and movement reliability between the rotary shaft 10 and the piston assembly 30.

As shown in FIG. 1, the illustrated fluid machine is a compressor including a dispenser component 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 outside the housing assembly 91, the upper cover assembly 94 is assembled to the upper end of the housing assembly 91, and the lower cover and mounting plate 95 are assembled at the lower end of the housing assembly 91, the motor assembly 92 and the pump The body assemblies 93 are all located inside the housing assembly 91 and the motor assembly 92 is disposed above the pump body assembly 93. The pump body assembly 93 of the compressor includes the upper flange 50, the lower flange 60, the cylinder 20, the rotating shaft 10, 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, the connecting shaft 331 is mounted on the lower flange 60, and the cylinder 20 is coaxially mounted with the piston sleeve 33, and the lower flange 60 is fixed to the cylinder 20. The sliding mating surface 111 of the rotating shaft 10 is fitted with a pair of parallel surfaces of the sliding holes 321 of the piston 32. The upper flange 50 fixes the upper half of the rotating shaft 10, and 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 guiding holes 311 are at least two, the two guiding holes 311 are disposed along the axial direction of the rotating shaft 10, and the pistons 32 are at least two, and each of the guiding holes 311 is correspondingly provided with a piston 32. At this time, the compressor is a single-cylinder multi-compression chamber compressor, and the torque fluctuation is relatively small compared with the same-displacement single-cylinder roller compressor.

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

It should be noted that, in this embodiment, when the piston 32 completes one-week movement, it will inhale and exhaust twice, so that the compressor has the characteristics of 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. 8 to 13, the cylinder wall of the cylinder 20 of the present invention has a compressed intake port 21 and a compressed exhaust port 22, and when the piston assembly 30 is in the intake position, the intake port 21 is compressed. The variable volume chamber 31 is electrically connected; when the piston assembly 30 is in the exhaust position, the variable volume chamber 31 is electrically connected to the 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. 8 to 13). 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-shaped section 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 where the compressed exhaust port 22 is located, and is compressed. The direction in which the intake buffer groove 23 extends is opposite to the direction in which the piston assembly 30 rotates.

The following describes the operation of the compressor:

As shown in Fig. 20, the compressor of the present invention is set using the principle of a cross slider mechanism. Wherein, the piston 32 acts as a slider in the cross slider mechanism, and the sliding engagement surface 111 of the piston 32 and the rotating shaft 10, the piston 32 and the guiding hole 311 of the piston sleeve 33 respectively serve as two connecting rods in the cross slider mechanism ₁ , l ₂ , this constitutes the main structure of the principle of the cross slider. And the axis O _{1 of the} rotating shaft 10 is eccentrically disposed with the axis O _{2 of the} cylinder 20, and the eccentricity of the two is fixed, and the two are respectively rotated about the respective axes. When the rotating shaft 10 rotates, the piston 32 linearly slides relative to the rotating shaft 10 and the piston sleeve 33 to achieve gas compression, and the piston assembly 30 as a whole rotates synchronously with the rotating shaft 10, and the piston 32 is at an eccentric distance e with respect to the axial center of the cylinder 20. Run within range. The stroke of the piston 32 is 2e, the cross-sectional area of the piston 32 is S, and the displacement of the compressor (i.e., the maximum suction volume) is V = 2 * (2e * S).

20, when the fluid machine of the above-described configuration is running, the rotary shaft 10 about the axis O ₁ of the rotation shaft 10; a cylinder 20 of the cylinder axis O ₂ 20 to rotate about the cylinder axis and the axis 20 of the shaft 10 The center of the heart is eccentrically disposed and the eccentric distance is fixed; the piston 32 of the piston assembly 30 rotates with the shaft 10 under the drive of the shaft 10 while simultaneously reciprocally sliding within the piston sleeve 33 of the piston assembly 30 in a direction perpendicular to the axis of the shaft 10.

The fluid machine operated by the above method constitutes a cross slider mechanism, which adopts the principle of a cross slider mechanism, wherein the piston 32 serves as a slider, and the sliding mating surface 111 of the rotating shaft 10 serves as a first connecting rod l ₁ and a piston. The guide hole 311 of the sleeve 33 serves as the second link ₁₂ (refer to Fig. 20).

Specifically, the axis O _{1 of the} rotating shaft 10 corresponds to the center of rotation of the first link ₁₁ , and the axis O _{2 of the} cylinder 20 corresponds to the center of rotation of the second link ₁₂ ; the slip fit surface 111 of the rotating shaft 10 Corresponding to the first link l ₁ , the guide hole 311 of the piston sleeve 33 corresponds to the second link l ₂ ; 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 and the axis O ₂ of the shaft 10 of the wiring ₁ is the diameter of the circle.

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 . As shown in FIG. 15, the center axis 15 of the rotating shaft and the piston sleeve axis 333 are separated by an eccentric distance e, and the piston mass center trajectory line is circular.

It should be noted that since the rotating shaft 10 is supported by the upper flange 50 and the piston sleeve 33, a cantilever supporting structure is formed.

As shown in FIG. 14 and FIG. 15, wherein the axis 15 of the rotating shaft and the piston sleeve axis 333 are separated by an eccentric distance e, the piston centroid trajectory line 322 has a circular shape.

Specifically, the motor assembly 92 drives the rotating shaft 10 to rotate, and the sliding mating surface 111 of the rotating shaft 10 drives the piston 32 to move, and the piston 32 drives the piston sleeve 33 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 rotating shaft 10 while reciprocating relative to the guiding hole 311 of the piston sleeve 33, and the two reciprocating motions are perpendicular to each other and simultaneously Thus, 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.

In addition, the compressor of the present invention also has the advantages of zero clearance volume and high volumetric efficiency.

Other use occasions: The compressor exchanges the suction and exhaust ports and can be used as an expander. That is, the exhaust port of the compressor is used as an intake port of the expander, high-pressure gas is introduced, and other push mechanisms are rotated, and after being expanded, the gas is exhausted through the intake port of the compressor (expander port of the expander).

When the fluid machine is an expander, the cylinder wall of the cylinder 20 has an expansion exhaust port and a first expansion intake port, and when the piston assembly 30 is in the intake position, the expansion exhaust port is electrically connected to the variable volume chamber 31; When the assembly 30 is in the exhaust position, the variable volume chamber 31 is electrically connected to the first expanded intake port. When the high pressure gas enters the variable volume chamber 31 through the first expansion inlet, the high pressure gas pushes the piston assembly 30 to rotate, the piston sleeve 33 rotates to drive the piston 32 to rotate, and at the same time, the piston 32 linearly slides relative to the piston sleeve 33, thereby The piston 32 is caused to rotate the rotating shaft 10. By connecting the rotating shaft 10 with other power consuming devices, the rotating shaft 10 can be outputted for work.

Preferably, the inner wall surface of the cylinder wall has an expanded exhaust buffer tank that communicates with the expanded exhaust port.

Further, the expanded exhaust buffer tank has an arc segment in a radial plane of the cylinder 20, and the expanded exhaust buffer tank extends from the expansion exhaust port to the side of the first inflation inlet, and the expanded exhaust buffer The slot extends in a direction opposite to the direction of rotation of the piston assembly 30.

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 fluid machine, comprising:

Upper flange (50);

Lower flange (60);

a cylinder (20), the cylinder (20) being interposed between the upper flange (50) and the lower flange (60);

a rotating shaft (10), an axis of the rotating shaft (10) is eccentrically disposed with an axial center of the cylinder (20) and an eccentric distance is fixed, and the rotating shaft (10) sequentially passes through the upper flange (50) and the Said cylinder (20);

a piston assembly (30) having a variable volume chamber (31) pivotally disposed within the cylinder (20) and having the shaft (10) The piston assembly (30) is drivingly coupled to vary the volume of the variable volume chamber (31).
The fluid machine of claim 1 wherein said piston assembly (30) comprises:

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

a piston (32), the piston (32) is slidably disposed in 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 fluid machine according to claim 2, wherein said piston (32) has a sliding hole (321) disposed in an axial direction of said rotating shaft (10), said rotating shaft (10) passing through said a sliding hole (321), the piston (32) being rotated by the rotating shaft (10) with the rotating shaft (10) while being in the axial direction perpendicular to the rotating shaft (10) at the piston The sleeve (33) slides back and forth.
The fluid machine according to claim 3, characterized in that the sliding hole (321) is a long hole or a waist hole.
The fluid machine according to claim 2, characterized in that the piston (32) has a sliding groove that is slidingly engaged with the rotating shaft (10).
The fluid machine according to claim 2, wherein said piston (32) has a pair of arcuate surfaces symmetrically disposed along a median 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 fluid machine according to claim 2, characterized in that the piston (32) has a cylindrical shape.
The fluid machine according to claim 2, wherein said piston sleeve (33) has a guide hole (311) disposed in a radial direction of said piston sleeve (33), said piston (32) sliding It is disposed in the guiding hole (311) to reciprocate linearly.
The fluid machine according to claim 8, wherein the orthographic projection of the guide hole (311) at the lower flange (60) has a pair of parallel straight line segments, the 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 fluid machine according to claim 2, wherein said piston sleeve (33) has a connecting shaft (331) projecting toward a side of said lower flange (60), said connecting shaft (331) being embedded It is disposed in the connecting hole of the lower flange (60).
The fluid machine 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 fluid machine according to claim 2, characterized in that the piston sleeve (33) has a second thrust surface (335) for supporting the rotating shaft (10), the orientation of the rotating shaft (10) An end surface on one side of the flange (60) is supported at the second thrust surface (335).
The fluid machine according to claim 3, characterized in that the rotating shaft (10) comprises:

Axis body (16);

a connector (17), the connector (17) being disposed at a first end of the shaft (16) and coupled to the piston assembly (30).
Fluid machine according to claim 13, characterized in that the joint (17) is quadrilateral in a plane perpendicular to the axis of the shaft (16).
Fluid machine according to claim 13, characterized in that the joint (17) has two symmetrical arrangement of slip-fitting faces (111).
The fluid machine according to claim 15, wherein said slip mating surface (111) is parallel to an axial plane of said rotating shaft (10), said slip mating surface (111) and said piston The inner wall surface of the sliding hole (321) of (32) is slidably fitted in the axial direction perpendicular to the rotating shaft (10).
The fluid machine according to claim 15, wherein said rotating shaft (10) has a lubricating oil passage (13) including an internal oil passage provided inside said rotating shaft (10) And an outer oil passage disposed outside the rotating shaft (10) and an oil passage hole (14) communicating the inner oil passage and the outer oil passage.
The fluid machine according to claim 17, wherein said slip fitting surface (111) has said outer oil passage extending in the axial direction of said rotating shaft (10).
The fluid machine according to any one of claims 1 to 18, wherein the upper flange (50) is disposed concentrically with the rotating shaft (10), and the upper flange (50) The axis is eccentric with the axis of the cylinder (20).
The fluid machine according to claim 19, wherein said lower flange (60) is disposed concentrically with said cylinder (20).
The fluid machine according to claim 1, wherein the cylinder wall of the cylinder (20) has a compressed intake port (21) and a 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 compressed exhaust port (22) when the piston assembly (30) is in the exhaust position.
The fluid machine according to claim 21, 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 fluid machine according to claim 22, 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 where the compressed exhaust port (22) is located.
A fluid machine according to any one of claims 21 to 23, wherein the fluid machine is a compressor.
The fluid machine according to claim 1, wherein a cylinder wall of the cylinder (20) has an expansion exhaust port and a first expansion air inlet.

The expansion exhaust port 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 expanded inlet when the piston assembly (30) is in the exhaust position.
The fluid machine according to claim 25, wherein an inner wall surface of the cylinder wall has an expanded exhaust buffer tank, and the expanded exhaust buffer tank communicates with the expansion exhaust port.
The fluid machine according to claim 26, wherein said expanded exhaust buffer tank has an arcuate section in a radial plane of said cylinder (20), and said expanded exhaust buffer tank is expanded by said expansion The exhaust port extends toward a side of the first inflation inlet.
A fluid machine according to any one of claims 25 to 27, wherein the fluid machine is an expander.
The fluid machine according to claim 8, wherein the guide holes (311) are at least two, and the two guide holes (311) are spaced apart in the axial direction of the rotating shaft (10), The pistons (32) are at least two, and one of the pistons (32) is correspondingly disposed in each of the guiding holes (311).
A heat exchange apparatus comprising a fluid machine, characterized in that the fluid machine is the fluid machine according to any one of claims 1 to 29.
A method for operating a fluid machine, comprising:

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

a cylinder (20) rotates about an axis O 2 of the cylinder (20), and an axis of the rotating shaft (10) is eccentrically disposed with an axial center of the cylinder (20) and an eccentric distance is fixed;

a piston (32) of the piston assembly (30) rotates with the shaft (10) under the drive of the shaft (10) and At the same time, it reciprocates in the piston sleeve (33) of the piston assembly (30) in a direction perpendicular to the axis of the rotating shaft (10).
The operating method according to claim 31, wherein the operating method adopts a principle of a cross slider mechanism, wherein the piston (32) serves as a slider, and a sliding mating surface of the 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 .