WO2017024868A1

WO2017024868A1 - Fluid machinery, heat exchange device, and method for operating fluid machinery

Info

Publication number: WO2017024868A1
Application number: PCT/CN2016/084331
Authority: WO
Inventors: 徐嘉; 杜忠诚; 杨森; 任丽萍; 孔令超; 张荣婷; 梁社兵; 邓丽颖; 许甲岿; 张金圈; 史正良
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: CN106704181B; CN106704181A

Abstract

Disclosed is a fluid machinery, which comprises: an upper flange (50); a lower flange (60); a cylinder (20) which is clamped between the upper flange (50) and the lower flange (60); a piston sleeve (33) which is pivotably provided in the cylinder (20); a piston sleeve shaft (34) which passes through the upper flange (50) and is fixedly connected to the piston sleeve (33); a piston (32) which is slidably provided in the piston sleeve (33) to form a variable volume cavity (31), the variable volume cavity (31) being located in a sliding direction of the piston (32); and a rotary shaft (10), an axis (15) of the rotary shaft (10) and an axis of the cylinder (20) being eccentrically arranged with the eccentric distance being fixed. The rotary shaft (10) successively passes through the lower flange (60) and the cylinder (20) to cooperate with the piston (32) in a slidable manner, under the driving action of the piston sleeve shaft (34), the piston sleeve (33) rotates synchronously with the piston sleeve shaft (34) to drive the piston (32) to slide in the piston sleeve (33) so as to change the volume of the variable volume cavity (31), and at the same time, the rotary shaft (10) rotates under the driving of the piston (32). The fluid machinery lowers the requirement for the structural strength of the rotary shaft and is able to effectively reduce the leakage between an end face of the piston sleeve and an end face of the upper flange. Further disclosed are a heat exchange device, and a method for operating a fluid machinery.

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 assembly drives the crankshaft to output power, and the crankshaft drives the piston to reciprocate in the cylinder to compress gas or liquid to perform work for the purpose of compressing gas or 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, a cylinder sandwiched between the upper flange and the lower flange; a piston sleeve, a piston sleeve The piston sleeve shaft is fixedly connected to the piston sleeve through the upper flange; the piston is slidably disposed in the piston sleeve to form a variable volume chamber, and the variable volume chamber is located on the sliding of the piston In the direction; the shaft, the axis of the shaft and the axis of the cylinder are eccentrically arranged and the eccentric distance is fixed, the shaft passes through the lower flange and the cylinder and the piston slide and cooperate with each other. Under the driving action of the piston sleeve shaft, the piston sleeve follows the piston sleeve shaft Synchronous rotation to drive the piston to slide within the piston sleeve to change the volume of the variable volume chamber, while the shaft rotates under the driving action of the piston.

Further, the piston has a sliding hole disposed through the axial direction of the rotating shaft, and the rotating shaft passes through the sliding hole, and the rotating shaft rotates with the piston sleeve and the piston under the driving of the piston, and the piston is in the piston sleeve along the axis perpendicular to the rotating 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, 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 first thrust surface of the piston sleeve facing the lower flange side is in contact with the surface of the lower flange.

Further, the rotating shaft has a sliding section that is slidingly engaged with the piston, the sliding section is located at one end of the rotating shaft away from the lower flange, and the sliding section has a sliding mating 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 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 piston sleeve shaft has a first lubricating oil passage penetratingly disposed along an axial direction of the piston sleeve shaft, the rotating shaft has a second lubricating oil passage communicating with the first lubricating oil passage, and at least a portion of the second lubricating oil passage is a rotating shaft In the internal oil passage, the second lubricating oil passage at the slip fitting surface is an external oil passage, the rotating shaft has an oil passage hole, and the internal oil passage communicates with the external oil passage through the oil passage hole.

Further, the upper flange and the cylinder are disposed concentrically, and the axis of the lower flange is eccentric with the axis of the cylinder.

Further, the fluid machine 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 and configured to support the rotating shaft, and the support plate has a second portion for supporting the rotating shaft Two pushes.

Further, the cylinder wall of the cylinder has a compressed air inlet and a compressed air outlet, and when the piston sleeve is in the intake position, the compression air inlet is electrically connected to the variable volume chamber; when the piston sleeve 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 both ends of the compressed intake buffer groove extend from a position of the compressed intake port to the compressed exhaust port.

Further, the fluid machine is a compressor.

Further, the cylinder wall of the cylinder has an expansion exhaust port and a first expansion air inlet, and when the piston sleeve is in the intake position, the expansion exhaust port is electrically connected to the variable volume chamber; when the piston sleeve is in the exhaust position, the cylinder is changed. 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 arc-shaped section in a radial plane of the cylinder, and both ends of the expanded exhaust buffer tank extend from the expanded exhaust port to a position of the first expanded 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 rotates with the rotating shaft under the driving of the rotating shaft and simultaneously reciprocates in the piston sleeve along the axis 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 .

By applying the technical solution of the present invention, by fixing the eccentric distance between the rotating shaft and the cylinder, the rotating shaft and the cylinder rotate around the respective axes during the movement, and the position of the center of mass is constant, thereby making the piston and the piston sleeve stable when moving in the cylinder. Continuously rotating, effectively alleviating the vibration of the fluid machine, 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 reliability of the heat exchange equipment. Sex. The fluid machine of the present invention drives the piston sleeve to rotate by the piston sleeve shaft and drives the piston to rotate, so that the piston slides in the piston sleeve to change the volume of the variable volume chamber, and the rotating shaft rotates under the driving action of the piston, thereby making the piston sleeve and The rotating shaft is subjected to bending deformation and torsional deformation, respectively, which reduces the overall deformation of the individual parts, reduces the structural strength requirement of the rotating shaft, and can effectively reduce the leakage between the end surface of the piston sleeve and the end surface of the upper flange.

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 piston sleeve 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 the lower flange in the present invention;

Figure 6 is a view showing the positional relationship between the axis of the rotating shaft and the axial center of the piston sleeve in the lower flange of Figure 5;

Figure 7 is a schematic view showing the mounting relationship of the rotating shaft, the piston, the piston sleeve and the piston sleeve shaft in the present invention;

Figure 8 is a schematic view showing the installation relationship of the piston sleeve and the piston sleeve shaft in the present invention;

Figure 9 is a schematic view showing the internal structure of Figure 8;

Figure 10 is a schematic view showing the assembly relationship between the rotating shaft and the piston in the present invention;

Figure 11 is a view showing the structure of a piston in the present invention;

Figure 12 is a view showing the structure of another angle of the piston in the present invention;

Figure 13 is a view showing the structure of a cylinder in the present invention;

Figure 14 shows a plan view of Figure 13;

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

Figure 16 is a schematic view showing the movement relationship of the cylinder, the piston sleeve, the piston and the rotating shaft in the present invention;

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 at the time of gas compression;

Figure 20 is a view showing the working state of the piston in the present invention before the start of exhausting;

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 at the end of exhausting;

Figure 23 is a view showing the structure of a support plate in the present invention;

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, the shaft; 11, the slip section; 111, the slip fit surface; 13, the second lubricating oil passage; 14, the oil passage hole; 15, the shaft axis of the shaft; 20, the cylinder; 21, the compressed air inlet; , compressed exhaust port; 23, compressed intake buffer tank; 31, variable volume chamber; 311, guiding hole; 32, piston; 321, sliding hole; 33, piston sleeve; 333, piston sleeve axis; a push surface; 34, piston sleeve shaft; 341, first lubricating oil passage; 50, upper flange; 60, lower flange; 61, support plate; 611, second thrust surface; 70, first fastening 80; second fastener; 322, piston centroid trajectory; 82, third fastener; 90, dispenser component; 91, housing assembly; 92, motor assembly; 93, pump body assembly; , 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 FIGS. 2 to 22, the fluid machine includes an upper flange 50, a lower flange 60, a cylinder 20, a rotating shaft 10, a piston sleeve 33, a piston sleeve shaft 34, and a piston 32, wherein the piston sleeve 33 is pivotally disposed In the cylinder 20, the piston sleeve shaft 34 is fixedly coupled to the piston sleeve 33 through the upper flange 50. 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. , the shaft 10, the axis of the shaft 10 is eccentrically arranged with the axis of the cylinder 20 and the eccentric distance is fixed, and the shaft 10 is sequentially slidably engaged with the piston 32 through the lower flange 60 and the cylinder 20, under the driving action of the sleeve shaft 34, The piston sleeve 33 rotates synchronously with the piston sleeve shaft 34 to drive the piston 32 to slide within the piston sleeve 33 to change the volume of the variable volume chamber 31 while the rotary shaft 10 is rotated by the driving of the piston 32. 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.

By fixing the eccentric distance of the rotating shaft 10 and the cylinder 20, the rotating shaft 10 and the cylinder 20 are rotated about their respective axes during the movement, and the position of the center of mass is constant, thereby making the piston 32 and the piston sleeve 33 stable when moving in the cylinder 20. Continuously rotating, effectively alleviating the vibration of the fluid machine, 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 reliability of the heat exchange equipment. Sex.

The fluid machine of the present invention drives the piston sleeve 33 to rotate by the piston sleeve shaft 34 and drives the piston 32 to rotate, so that the piston 32 slides within the piston sleeve 33 to change the volume of the variable volume chamber 31, while the shaft 10 is driven by the piston 32. The lower rotation causes the piston sleeve 33 and the rotating shaft 10 to undergo bending deformation and torsional deformation, respectively, which reduces the overall deformation of the single part, reduces the structural strength requirement of the rotating shaft 10, and can effectively reduce the end face and the upper method of the piston sleeve 33. Leakage between the ends of the blue 50.

It should be noted that the upper flange 50 and the cylinder 20 are disposed concentrically, and the axial center of the lower flange 60 is eccentric from the axial center of 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 sleeve 33 has a characteristic of good motion stability.

In the preferred embodiment shown in FIG. 2 to FIG. 22, the piston 32 is slidably engaged with the rotating shaft 10, and the piston 32 is driven by the piston sleeve 33 to rotate the rotating shaft 10, and the piston 32 has a linear motion with respect to the rotating shaft 10. . Since the piston 32 is slidably coupled with the piston sleeve 33, the movement of the piston 32 is effectively prevented from being jammed, 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.

Since the cross slider mechanism is formed between the piston 32, the piston sleeve 33, the cylinder 20 and the rotating shaft 10, the movement of the piston 32, the piston sleeve 33 and the cylinder 20 is stabilized and continuous, and the volume change of the variable volume chamber 31 is regular. Thereby ensuring the operational stability of the fluid machine, thereby improving the operational reliability of the heat exchange equipment.

The piston 32 of the present invention has a sliding hole 321 which is disposed through the axial direction of the rotating shaft 10, and the rotating shaft 10 passes through the sliding hole 321, and the rotating shaft 10 rotates with the piston sleeve 33 and the piston 32 under the driving of the piston 32, and the piston 32 The reciprocating sliding in the piston sleeve 33 in the axial direction perpendicular to the rotating shaft 10 (please refer to Figs. 10 to 12, Figs. 16 to 22). 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 sliding groove disposed toward the side of the rotating 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. The slip groove is a linear chute, and the direction of the slip groove extends 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.

10 to 12 and 16 to 22, the piston 32 has a pair of arcuate surfaces symmetrically disposed along the center plane of the piston 32, the arcuate surface being adaptively fitted to the inner surface of the cylinder 20, and the curved surface The radius of curvature of the camber is equal to twice 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.

As shown in FIGS. 7 to 9, the piston sleeve 33 has a guide hole 311 which is provided in the radial direction of the piston sleeve 33, and 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 fluid machine.

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. 18, 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. 2, the rotating shaft 10 has a sliding section 11 that is slidably engaged with the piston 32. The sliding section 11 is located at one end of the rotating shaft 10 away from the lower flange 60, and the sliding section 11 has a sliding mating surface 111. Since the rotating shaft 10 is slidably engaged with 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.

Preferably, the slip section 11 has two symmetrical arrangement of slip fit 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 FIG. 2, the slip fitting surface 111 is parallel to the axial plane of the rotating shaft 10, and the sliding 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 rotating shaft 10.

The piston sleeve shaft 34 of the present invention has a first lubricating oil passage 341 penetratingly disposed in the axial direction of the piston sleeve shaft 34. The rotating shaft 10 has a second lubricating oil passage 13 communicating with the first lubricating oil passage 341, and the second lubricating oil. At least a portion of the track 13 is the internal oil passage of the rotating shaft 10. Due to at least a part of the internal oil passage of the second 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. 2, the second lubricating oil passage 13 at the slip fitting surface 111 is an external oil passage. Since the second lubricating oil passage 13 at the slip matching 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 preventing the friction between the two from being excessively worn and thus improving. The smoothness of both sports.

As shown in FIG. 2, the rotating shaft 10 has an oil passage hole 14, and the internal oil passage communicates with the external 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 connected, and the oil passage hole 14 can also be injected into the second lubricating oil passage 13, thereby ensuring the convenience of oil filling of the second lubricating oil passage 13.

As shown in FIGS. 2 and 23, the fluid machine of the present invention further includes a support plate 61 which is disposed on an end surface of the lower flange 60 on the side away from the cylinder 20, and the support plate 61 is coaxial with the lower flange 60. The core is disposed and supported for supporting the rotating shaft 10, and the rotating shaft 10 is supported on the supporting plate 61 through a through hole on the lower flange 60, and the supporting plate 61 has a second thrust surface 611 for supporting the rotating shaft 10. Since the support plate 61 is provided for supporting the rotary shaft 10, the connection reliability between the components is improved.

As shown in FIGS. 2 to 4, the support plate 61 is coupled to the lower flange 60 by a third fastener 82.

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

As shown in FIG. 5, the lower flange 60 is provided with four pump body screw holes for the second fastener 80 to be pierced, and three support disk thread holes for the third fastener 82 to pass through, four The circle formed by the center of the pump body screw hole is eccentric with the center of the bearing, and the amount of eccentricity is e. This amount determines the eccentric amount of the pump body assembly. After the piston sleeve 33 rotates for one week, the gas volume V=2*2e*S, Where S is the cross-sectional area of the main structure of the piston 32; the center of the threaded hole of the support disk coincides with the axis of the lower flange 60, and the support plate 61 is fixed with the third fastener 82.

As shown in FIG. 2, the support plate 61 has a cylindrical structure, and three screw holes for the third fastener 82 are evenly distributed. The surface of the support plate 61 facing the shaft 10 has a certain roughness to the shaft 10 The bottom of the fit.

As shown in Figures 1 through 22, the illustrated fluid machine is a compressor that includes a dispenser component 90, a housing assembly 91, a motor assembly 92, a pump assembly 93, an upper cover assembly 94, and a lower cover. The mounting plate 95, wherein the dispenser member 90 is disposed outside the housing assembly 91, the upper cover assembly 94 is assembled at 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 Both the 92 and pump body assembly 93 are 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 above-described upper flange 50, lower flange 60, cylinder 20, rotating shaft 10, piston 32, piston sleeve 33, piston sleeve shaft 34, and the like.

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 pilot hole 311, the cylinder 20 is mounted coaxially with the piston sleeve 33, and the lower flange 60 is fixed to the cylinder 20, and the sliding mating surface 111 of the rotating shaft 10 and the piston 32 A pair of parallel surfaces of the sliding holes 321 are fitted together, and the upper flange 50 fixes the piston sleeve shaft 34 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 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 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. 13 and 14 and 16 to 22, the cylinder wall of the cylinder 20 of the present invention has a compressed intake port 21 and a compressed exhaust port 22 when the piston sleeve 33 is in the intake position. The compressed air inlet 21 is electrically connected to the variable volume chamber 31; when the piston sleeve 33 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 that communicates with the compressed intake port 21 (please refer to FIGS. 13 and 14, 16 to 22). 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 both ends of the compressed intake buffer groove 23 are extended from the compressed intake port 21 to the compressed exhaust port 22. .

Alternatively, with respect to the compressed intake port 21, the arc length of the extended portion of the compressed intake buffer groove 23 in the same direction as the rotational direction of the piston sleeve 33 is larger than the arc length of the extension portion in the opposite direction.

The following describes the operation of the compressor:

As shown in Fig. 24, the compressor of the present invention is set using the principle of a cross slider mechanism. Wherein the shaft axis O ₁ 10 O 20 and the cylinder axis of the _second eccentric is provided, and both fixed eccentricity, and both are rotated about their 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 sleeve 33 rotates synchronously with the rotating shaft 10, and the piston 32 is in the range of the eccentric distance e with respect to the axial center of the cylinder 20. Running inside. 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). The piston 32 is equivalent to the slider in the cross slider mechanism, and the piston-guide hole 311 and the piston 32 - the sliding mating surface 111 of the rotating shaft 10 respectively serve as the two connecting rods l ₁ and l _{2 of the} cross slider, thus forming a cross The main structure of the slider principle.

24, 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 set and the eccentric distance is fixed; the piston 32 rotates with the rotating shaft 10 under the driving of the rotating shaft 10 and simultaneously reciprocates in the piston sleeve 33 in the axial direction perpendicular to the rotating 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 a second link ₁₂ (refer to Fig. 24).

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.

As shown in FIG. 6 and FIG. 16 , the axial center 15 of the rotating shaft and the piston sleeve axial center 333 are separated by an eccentric distance e, and the piston centroid trajectory line 322 is circular.

The piston sleeve 33 is eccentrically mounted with the rotating shaft 10, and the piston sleeve shaft 34 is connected to the motor assembly 92. The motor assembly 92 directly drives the piston sleeve 33 to rotate, which belongs to the piston sleeve driving structure. The piston sleeve 33 rotates to drive the piston 32 to rotate, and the piston 32 drives the rotating shaft 10 to rotate through the rotating shaft supporting surface. The piston 32, the piston sleeve 33 and the rotating shaft 10 cooperate with other pump parts to complete the suction, compression and exhaust during the rotation process. Process, one cycle is 2π. The shaft 10 rotates clockwise.

Specifically, the motor assembly 92 drives the piston sleeve shaft 34 for rotational movement, and the pilot hole 311 drives the piston 32 to perform a rotational motion, but the piston 32 reciprocates only relative to the piston sleeve 33; the piston 32 further drives the shaft 10 for rotational movement, but The piston 32 also reciprocates only with respect to the rotating shaft 10, and this reciprocating motion is perpendicular to the reciprocating motion of the piston sleeve 33-piston 32. During the reciprocating motion, the entire pump body assembly completes the process of inhaling, compressing, and exhausting. During the movement of the piston, the two mutually perpendicular reciprocating motions of the piston 32-piston sleeve 33, the piston 32-the shaft 10, the center line of the piston 32 is circular, the diameter of the circle is equal to the amount of eccentricity e, and the axis is at the shaft 10 At the midpoint of the center of the piston sleeve 33, the rotation period is π.

The piston forms two cavities in the guiding hole 311 of the piston sleeve 33 and the inner circular surface of the cylinder 20. The piston sleeve 33 rotates once, and the two cavities respectively perform the processes of inhaling, compressing and exhausting, and the difference lies in the two cavities. The suction and exhaust compression has a phase difference of 180°. Taking one of the cavities as an example to describe the process of inhaling, exhausting, and compressing the pump body assembly 93, as follows: when the cavity is in communication with the compressed air inlet 21, inhalation is started (please refer to FIG. 17 and FIG. 18); 33 continues to drive the piston 32, the shaft 10 rotates clockwise, when the variable volume chamber 31 is out of the compressed air inlet 21, the entire inhalation ends, at this time the cavity is completely sealed and begins to compress (please refer to Figure 19); continue to rotate, the gas is continuously compressed When the variable volume chamber 31 is in communication with the compressed exhaust port 22, the exhaust gas is started (please refer to FIG. 20); the rotation is continued, and the air is continuously exhausted while continuously compressing until the variable volume chamber 31 is completely separated from the compressed exhaust port 22, and is completed. The entire inhalation, compression, and exhaust process (please refer to Figures 21 and 22); then the variable volume chamber 31 is rotated by a certain angle and then connected to the compressed intake port 21 to enter the next cycle.

The pump body assembly 93 in the present invention is a constant pressure ratio pump body structure, and the two variable volume chambers 31 are V=2*2e*S, and S is a piston cross-sectional area.

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

It should be emphasized that, in the solution that the rotating shaft passes through the upper flange 50, the cylinder 20 and the lower flange 60 in sequence, the compressor of the present invention uses the piston sleeve 33 to drive the piston 32 to rotate, and the piston 32 drives the rotating shaft 10 to rotate. The piston sleeve 33 and the rotating shaft 10 respectively undergo bending deformation and torsional deformation, which can effectively reduce deformation wear; and can effectively reduce leakage between the end surface of the piston sleeve 33 and the end surface of the upper flange 50. The focus of this case is that the piston sleeve shaft 34 and the piston sleeve 33 are integrally formed. The upper and lower flanges are disposed off-axis to eccentrically rotate the shaft 10 and the sleeve shaft 34.

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 sleeve 33 is in the intake position, the expansion exhaust port is electrically connected to the variable volume chamber 31; When the sleeve 33 is in the exhaust position, the variable volume chamber 31 is electrically connected to the first inflation inlet. When the high pressure gas enters the variable volume chamber 31 through the first expansion air inlet, the high pressure gas pushes the piston sleeve 33 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-shaped section in the radial plane of the cylinder 20, and both ends of the expanded exhaust buffer tank extend from the expanded exhaust port to the position of the first expanded intake port.

Optionally, the arc length of the extended exhaust buffer tank in the same direction as the direction of rotation of the piston sleeve 33 is smaller than the arc length of the extension in the opposite direction.

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

a piston sleeve shaft (34), the piston sleeve shaft (34) being fixedly connected to the piston sleeve (33) through the upper flange (50);

a piston (32), 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 a sliding direction of the piston (32) on;

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 lower flange (60) and the The cylinder (20) is in sliding engagement with the piston (32). Under the driving action of the piston sleeve shaft (34), the piston sleeve (33) rotates synchronously with the piston sleeve shaft (34) to drive The piston (32) slides within the piston sleeve (33) to change the volume of the variable volume chamber (31) while the shaft (10) rotates under the driving action of the piston (32).
The fluid machine according to claim 1, wherein said piston (32) has a sliding hole (321) penetratingly disposed in an axial direction of said rotating shaft (10), said rotating shaft (10) passing through said a sliding hole (321), the rotating shaft (10) is rotated by the piston (32) with the piston sleeve (33) and the piston (32) while the piston (32) is vertical Reciprocating sliding in the piston sleeve (33) in the axial direction of the rotating shaft (10).
The fluid machine according to claim 2, wherein the sliding hole (321) is a long hole or a waist hole.
The fluid machine according to claim 1, 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 1, wherein said piston (32) has a cylindrical shape.
The fluid machine according to claim 1, 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 6, 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 1, 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 any one of claims 1 to 8, characterized in that the rotating shaft (10) has a sliding section (11) which is slidably engaged with the piston (32), the sliding section ( 11) Located at one end of the rotating shaft (10) away from the lower flange (60), and the sliding section (11) has a sliding mating surface (111).
The fluid machine according to claim 9, characterized in that the slip mating faces (111) are symmetrically disposed on both sides of the slip section (11).
The fluid machine according to claim 9, 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 9, wherein said piston sleeve shaft (34) has a first lubricating oil passage (341) disposed in an axial direction of said piston sleeve shaft (34), said shaft (10) having a second lubricating oil passage (13) communicating with the first lubricating oil passage (341), at least a portion of the second lubricating oil passage (13) being an internal oil passage of the rotating shaft (10) The second lubricating oil passage (13) at the slip mating surface (111) is an outer oil passage, and the rotating shaft (10) has an oil passage hole (14) through which the inner oil passage passes An oil passage hole (14) is in communication with the outer oil passage.
The fluid machine according to any one of claims 1 to 8, wherein the upper flange (50) and the cylinder (20) are disposed concentrically, and the lower flange (60) The axis is eccentric with the axis of the cylinder (20).
The fluid machine according to claim 13, wherein said fluid machine further comprises a support plate (61), said support plate (61) being disposed away from said cylinder (20) of said lower flange (60) On one end face, and the support plate (61) is disposed concentrically with the lower flange (60) and used to support the rotating shaft (10), the support plate (61) has a support for supporting The second thrust surface (611) of the rotating shaft (10).
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 sleeve (33) is in an intake position;

The variable volume chamber (31) is electrically connected to the compressed exhaust port (22) when the piston sleeve (33) is in the exhaust position.
The fluid machine according to claim 15, 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 16, wherein said compressed intake buffer tank (23) has an arcuate section in a radial plane of said cylinder (20), and said compressed intake buffer tank ( Both ends of 23) extend from the compressed intake port (21) to the position of the compressed exhaust port (22).
A fluid machine according to any one of claims 15 to 17, 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 sleeve (33) is in an intake position;

The variable volume chamber (31) is electrically connected to the first expansion inlet when the piston sleeve (33) is in the exhaust position.
The fluid machine according to claim 19, wherein an inner wall surface of the cylinder wall has an expansion exhaust buffer tank, and the expansion exhaust buffer tank communicates with the expansion exhaust port.
The fluid machine according to claim 20, wherein said expanded exhaust buffer tank has an arcuate section in a radial plane of said cylinder (20), and both ends of said expanded exhaust buffer tank Extending from the expansion exhaust port to a position of the first inflation inlet.
A fluid machine according to any one of claims 19 to 21, wherein the fluid machine is an expander.
The fluid machine according to claim 6, wherein the guide holes (311) are at least two, and the two guide holes (311) are disposed along an axial interval 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 23.
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;

The piston (32) rotates with the rotating shaft (10) under the driving of the rotating shaft (10) and simultaneously reciprocates in the piston sleeve (33) in a direction perpendicular to the axis of the rotating shaft (10).
The operating method according to claim 25, wherein the operating method adopts a principle of a cross slider mechanism, wherein the piston (32) functions 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 .