WO2022016934A1 - 压缩机和空调器 - Google Patents

压缩机和空调器 Download PDF

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Publication number
WO2022016934A1
WO2022016934A1 PCT/CN2021/089286 CN2021089286W WO2022016934A1 WO 2022016934 A1 WO2022016934 A1 WO 2022016934A1 CN 2021089286 W CN2021089286 W CN 2021089286W WO 2022016934 A1 WO2022016934 A1 WO 2022016934A1
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WO
WIPO (PCT)
Prior art keywords
exhaust
flange
compressor
main shaft
groove
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2021/089286
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English (en)
French (fr)
Inventor
董明珠
胡余生
魏会军
徐嘉
任丽萍
万鹏凯
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Gree Electric Appliances Inc of Zhuhai
Original Assignee
Gree Electric Appliances Inc of Zhuhai
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Gree Electric Appliances Inc of Zhuhai filed Critical Gree Electric Appliances Inc of Zhuhai
Publication of WO2022016934A1 publication Critical patent/WO2022016934A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C18/3441—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C18/3445—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the vanes having the form of rollers, slippers or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
    • F04C29/128—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type of the elastic type, e.g. reed valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/60—Shafts

Definitions

  • the present disclosure relates to the technical field of compressors, in particular to a compressor and an air conditioner.
  • the patent No. 201510044276.4 discloses a compressor exhaust structure.
  • the exhaust passage 30 opened on the main shaft is communicated with the guide passage 20 opened on the flange to realize the exhaust at the end of the compressor.
  • the main exhaust is achieved through the exhaust port 10 on the flange.
  • the patent No. 201710916718.9 proposes a compressor structure.
  • the main exhaust port involved adopts the same principle as the patent 201510044276.4.
  • the vane In order to ensure that the area of the exhaust port of the compressor is as large as possible and reduce the exhaust loss, the requirements The vane must completely cover the exhaust port as it sweeps across the exhaust port, so a diamond-shaped exhaust port configuration is required for larger exhaust ports.
  • the design pressure ratio should be greater than the pressure ratio of all operating conditions of the compressor, otherwise there will be under-compression in some operating conditions. (The problem of exhausting when the exhaust pressure is not reached), the design requires the communication angle to be as far back as possible.
  • the exhaust passage only plays the role of auxiliary exhaust, and the utilization rate is not high.
  • the exhaust port on the flange adopts a diamond-shaped structure, and the number of exhaust ports needs to be increased.
  • the number of valve plate components also increases, which increases the number of compressor parts, increases the cost and hidden dangers of reliability; at the same time, the exhaust port structure is opened on the flange, which reduces the rigidity of the flange and may cause wear and reliability problems; in addition, due to the exhaust port structure The position of the air port is fixed.
  • the airflow at the exhaust port may affect the operation of the sliding vane, resulting in an unstable state caused by the inclination of the sliding vane or the change of force, which affects the reliability of the compressor.
  • the exhaust valve is opened N times for each rotation of the compressor (N is the number of slides), and the valve is prone to reliability problems such as breakage during high-frequency operation.
  • the exhaust port of the compressor in the technology known to the inventor is arranged on the flange and is opposite to the compression cavity, when the cavity passes through a flange exhaust port and is closed after exhausting, the area of the exhaust port changes abruptly , resulting in a sudden change in the discharge speed of the compressor, and there is a big hidden danger to the reliability of the compressor.
  • the present disclosure researches and designs a compressor and an air conditioner.
  • the technical problem to be solved by the present disclosure is to overcome the defect that the compressor in the technology known to the inventor has a sudden change in the discharge port area, which leads to a sudden change in the discharge speed of the compressor, thereby providing a compressor and an air conditioner.
  • a compressor which includes:
  • a main shaft, a cylinder, a flange and a sliding vane the main shaft includes a convex part, the convex part, the cylinder, the flange and the sliding vane together form a compression cavity, and at least one main shaft exhaust port is opened on the convex part corresponding to each compression cavity,
  • the flange is provided with a flange exhaust port, one end of each main shaft exhaust port is communicated with the compression chamber, and the other end can be communicated with the flange exhaust port during the rotation of the main shaft for exhausting, and the main shaft exhaust port can be exhausted.
  • An exhaust valve assembly is arranged in the air port, and the exhaust valve assembly can automatically exhaust according to the pressure in the compression chamber;
  • the main shaft exhaust port includes radial exhaust holes and axial exhaust holes.
  • the radial exhaust holes are opened on the radial outer side of the convex portion and are opened along the radial direction, and the axial exhaust holes are opened in the axial direction of the convex portion.
  • the end face is opened along the axial direction, and the axial exhaust hole is communicated with the radial exhaust hole, so that the air flow passes through the compression chamber, the radial exhaust hole and the axial exhaust hole in sequence;
  • the exhaust valve assembly includes a baffle plate, a valve block and an elastic part, the baffle plate is embedded in the radial exhaust hole from the end face of the convex part, the valve block and the elastic part are arranged in the radial exhaust hole, and one end of the valve block is formed with a The accommodating cavity to accommodate at least part of the elastic member is arranged therein, the other end of the valve block is arranged opposite to the baffle plate, the baffle plate is provided with a valve port, and the valve block can open or close the valve port by reciprocating motion, so that the compression cavity and the shaft Toggles between on and off to the vent.
  • the valve block includes a head portion and a tail portion, the head portion is arranged opposite to the baffle plate, an annular first flow groove is formed at the position where the head portion and the tail portion meet, and the first flow groove can be connected to the axial exhaust hole.
  • a second flow groove is opened at the tail, one end of the second flow groove is communicated with the first flow groove, and the other end is communicated with the accommodating cavity, and the accommodating cavity is formed in the interior of the tail.
  • the valve block has a cylindrical structure
  • the first flow groove is an annular groove opened along the circumference of the cylinder
  • the second flow groove is opened along the axial direction of the cylinder on the outer peripheral surface of the tail portion
  • the strip groove, the second flow groove communicates with the accommodating cavity at the end away from the annular groove.
  • At least two second flow grooves are arranged at intervals along the circumference of the cylinder.
  • an insert groove is formed on the end surface of the convex portion, the thickness of the insert groove is adapted to the thickness of the baffle plate, and the baffle plate is clamped into the convex portion from the insert groove.
  • the thickness B of the baffle satisfies 1 ⁇ B ⁇ 5mm.
  • the caulking groove is parallel to the central axis of the main shaft, and the caulking groove is perpendicular to the central axis of the radial vent hole.
  • At least two radial exhaust holes are arranged at intervals along the axial direction of the main shaft, and an exhaust valve assembly is disposed in each radial exhaust hole; and/or, an axial exhaust hole It penetrates the upper and lower end surfaces of the convex portion in the axial direction of the main shaft.
  • At least one sliding vane slot is further opened on the convex portion, the sliding vane is arranged in the sliding vane slot, and the main shaft exhaust port is arranged at a position relatively close to the compression end end of the sliding vane slot in the circumferential direction.
  • the main shaft exhaust port when there are more than two vane slots, is disposed at a position between two adjacent vane slots in the circumferential direction, and the main shaft exhaust port is relatively close to the vane slot located at the end of compression s position.
  • the flange exhaust port includes a flange exhaust slot and a flange exhaust hole
  • the flange exhaust slot is provided on an axial end face of the flange that is connected to the convex portion and is located along the axial direction Open
  • the flange exhaust hole is arranged on the other axial end face of the flange opposite to the convex part and is opened along the axial direction
  • one end of the flange exhaust groove is communicated with the flange exhaust hole
  • the flange exhaust The other end of the slot can communicate with the main shaft exhaust port during the rotation of the main shaft.
  • the flange exhaust slot is an arc-shaped slot extending in the circumferential direction, the flange exhaust hole is at least one, and the at least one flange exhaust hole communicates with the flange exhaust slot.
  • the initial angle of the flange exhaust groove is ⁇
  • the suction end angle of the pump body cavity of the compressor is ⁇ , and satisfies: ⁇ .
  • the flange includes an upper flange and a lower flange, the upper flange is provided with a flange exhaust port and/or the lower flange is provided with a flange exhaust port;
  • the exhaust valve assembly when the pressure in the compression chamber is greater than or equal to the preset exhaust pressure, the exhaust valve assembly is opened to perform exhaust, and when the pressure in the compression chamber is less than the preset exhaust pressure, the exhaust valve assembly is closed without exhaust;
  • the compressor is a vane compressor.
  • the head when the valve block includes the first flow groove and the second flow groove, the head is subjected to the pressure P in the compression cavity introduced by the radial exhaust hole, and the elastic force exerted by the elastic member on the valve block is F , the exhaust pressure introduced into the accommodating cavity from the outside of the axial exhaust hole through the first flow slot and the second flow slot is Pd, when P*S1>Pd*S2+F, the exhaust valve assembly is opened to exhaust , when P*S1 ⁇ Pd*S2+F, the exhaust valve assembly is closed without exhausting, where S1 is the area of the radial exhaust hole, and S2 is the area of the valve block.
  • the present disclosure also provides an air conditioner including the compressor of any preceding item.
  • the present disclosure effectively cancels the existing exhaust structure provided at the position corresponding to the compression chamber on the flange. Since the convex part rotates together with the main shaft, the main shaft discharges The air port is always located between the two sliding vanes, and the exhaust valve assembly is arranged inside the main shaft exhaust port to automatically open the exhaust valve assembly to exhaust or close the exhaust according to the size of the compression chamber.
  • the exhaust valve assembly When the pressure in the compression chamber is greater than or equal to the preset exhaust pressure, the exhaust valve assembly is opened to exhaust, and when the pressure in the compression chamber is less than the preset exhaust pressure, the exhaust valve The components are closed without exhausting; that is, the structural design of the main shaft exhaust port + exhaust valve assembly + flange exhaust port is used to effectively ensure that the number and area of exhaust ports in each compression chamber are fixed, which can meet the compressor discharge requirements. At the same time as the air speed is required, it is ensured that the compressor operates normally under all working conditions, and the discharge speed changes continuously;
  • the exhaust valve plate is opened N times (N is the number of sliding plates), and the valve plate is prone to reliability problems such as fracture during high-frequency operation.
  • FIG. 1 is an exploded structural view of a compressor pump body part of the present disclosure
  • FIG. 2 is a top view of the compressor pump body portion of the present disclosure
  • FIG. 3 is a cross-sectional view of the pump body in the suction/compression stage of the compressor of the present disclosure
  • Fig. 4 is a partial enlarged view of the position of the exhaust port in the suction/compression stage of the present disclosure (a partial enlarged view of part A of Fig. 3, position 1 in Fig. 2, the valve block is not opened);
  • FIG. 5 is a partial enlarged view of the position of the exhaust port in the exhaust stage of the present disclosure (a partial enlarged view of part A of FIG. 3, position 2 in FIG. 2, the valve block is open);
  • FIG. 6 is a perspective view, top view, bottom view and A-A cross-sectional view of the upper flange of the present disclosure
  • FIG. 7 is an enlarged view of a perspective, front view, top view and part B of the main shaft of the compressor of the present disclosure
  • FIG. 8 is a perspective, front view and longitudinal cross-sectional structural view of a valve block of the compressor of the present disclosure
  • FIG. 9 is a perspective and front structural view of a block post of the compressor of the present disclosure.
  • FIG. 10 is a perspective view, a front cross-sectional view and a top view of the assembly of the main shaft and the valve assembly of the compressor of the present disclosure
  • Main shaft 11. Convex; 111. Blocking post groove; 12. Slider groove; 100. Compression chamber; 2. Air cylinder; 3. Flange; 31. Upper flange; 32. Lower flange; 4. Slider Sheet; 5. Main shaft exhaust port; 51, Radial exhaust hole; 52, Axial exhaust hole; 6, Flange exhaust port; 61, Flange exhaust slot; 62, Flange exhaust hole; 7 71, valve block; 710, accommodating cavity; 711, head; 712, tail; 713, first flow groove; 714, second flow groove; 72, elastic part; 73, blocking part; 731 , blocking parts; 8, cover plate.
  • a compressor comprising:
  • Main shaft 1 cylinder 2, flange 3 and sliding vane 4.
  • the main shaft 1 includes a convex part 11.
  • the convex part 11, the cylinder 2, the flange 3 and the sliding vane 4 together form a compression chamber 100.
  • the convex part 11 is connected to each compression chamber.
  • each main shaft exhaust port 5 is communicated with the compression chamber 100, and the other end can be connected with the flange exhaust port 6 during the rotation of the main shaft.
  • the main shaft exhaust port 5 is provided with an exhaust valve assembly 7, and the exhaust valve assembly 7 can automatically exhaust according to the pressure in the compression chamber 100;
  • the main shaft exhaust port 5 includes a radial exhaust hole 51 and an axial exhaust hole 52.
  • the radial exhaust hole 51 is opened on the radial outer side of the convex portion 11 and is opened along the radial direction, and the axial exhaust hole 52 is opened. Opened on the axial end face of the convex portion 11 and along the axial direction, the axial exhaust hole 52 communicates with the radial exhaust hole 51 , so that the air flow from the compression chamber 100 , the radial exhaust hole 51 and the axial exhaust hole 52 pass in turn;
  • the exhaust valve assembly 7 includes a baffle 73 , a valve block 71 and an elastic member 72 (optionally, a spring).
  • the valve block 71 is disposed in the radial exhaust hole 51, and one end of the valve block 71 is formed with an accommodating cavity 710 to accommodate at least part of the elastic member 72 therein.
  • the other end of the valve block 71 is disposed opposite to the baffle plate 73.
  • a valve port 731 is provided on the valve block 71 , and the valve block 71 can reciprocate to open or close the valve port 731 , so that the compression chamber 100 and the axial exhaust hole 52 are switched between communication and closed communication.
  • the present disclosure effectively cancels the existing exhaust structure provided at the position corresponding to the compression chamber on the flange. Since the convex part rotates together with the main shaft, the main shaft discharges The air port is always located between the two sliding vanes, and the exhaust valve assembly is arranged inside the main shaft exhaust port to automatically open the exhaust valve assembly to exhaust or close the exhaust according to the size of the compression chamber.
  • the exhaust valve assembly 7 When the pressure in the compression chamber 100 is greater than or equal to the preset exhaust pressure, the exhaust valve assembly 7 is opened to exhaust, and when the pressure in the compression chamber 100 is less than the preset exhaust pressure, the exhaust valve assembly 7 is closed without Exhaust; that is, the structural design of the main shaft exhaust port + exhaust valve assembly + flange exhaust port is used to effectively ensure that the number and area of exhaust ports in each compression chamber are fixed, and can meet the compressor exhaust speed requirements. At the same time, it is ensured that the compressor operates normally under all working conditions, and the discharge speed changes continuously.
  • the main shaft exhaust port of the present disclosure includes a radial exhaust hole, which can communicate with and introduce gas from the compression chamber through the radial exhaust hole, and the axial exhaust hole is used to communicate and introduce the gas from the radial exhaust hole to the compression chamber.
  • Effective exhaust is carried out in the flange exhaust port, which effectively replaces and cancels the structure in which the exhaust port is set on the flange opposite to the position of the compression chamber in the technology known to the inventor, effectively ensuring the number of exhaust ports in each compression chamber. And the area is fixed, and the exhaust velocity changes continuously.
  • the present disclosure forms an exhaust valve structure by cooperating with a baffle plate, a valve block and an elastic member, and can utilize the elastic force of the elastic member to abut the valve block at the radial exhaust hole in the initial state to close the exhaust valve when the pressure in the compression chamber is low.
  • valve port 731 Since the valve port 731 is opened on the baffle plate 73 , and the baffle plate 73 is embedded into the convex portion 11 from the end face of the convex portion 11 , and is located on the path of the radial exhaust hole 51 , the valve port 731 makes the two ends of the baffle plate 73 The radial exhaust holes 51 communicate with each other. This structure enables the baffle plate 73 to be inserted into the radial exhaust hole 51 from the side of the radial exhaust hole 51, and the baffle plate 73 can be used to stop the valve block 71 without using the radial exhaust hole 51 itself.
  • the valve block 71 is constructed to form a stop, so the arrangement of the radial exhaust hole 51 can be facilitated, so that the valve block 71 can be directly loaded into the radial exhaust hole 51 from the inlet of the radial exhaust hole 51, reducing the The installation difficulty of the valve block 71 is reduced, so that the installation of the exhaust valve assembly 7 is simpler and more convenient.
  • Surface contact can be achieved between the baffle plate 73 and the valve block 71 at the valve port 731 , thereby improving the overall sealing performance of the exhaust valve assembly 7 and improving the working performance of the exhaust valve assembly 7 .
  • the exhaust valve plate is opened N times (N is the number of sliding plates), and the valve plate is prone to reliability problems such as fracture during high-frequency operation.
  • the main shaft of the present disclosure is provided with an exhaust port, an exhaust valve assembly is installed, and a flange exhaust slot and a flange exhaust hole are arranged on the flange.
  • the valve block 71 includes a head 711 and a tail 712, the head 711 is disposed opposite the baffle 73, and an annular first flow groove 713 is formed where the head 711 and the tail 712 meet.
  • the groove 713 can be communicated with the axial exhaust hole 52 to introduce exhaust pressure from the axial exhaust hole 52.
  • a second flow groove 714 is formed on the outer peripheral surface of the tail portion 712, and one end of the second flow groove 714 is connected to the first flow groove 714.
  • the flow groove 713 is in communication, and the other end is in communication with the accommodating cavity 710 , and the accommodating cavity 710 is formed inside the tail portion 712 .
  • valve block of the present disclosure that is, through the structural form of the head and the tail, the end of the radial exhaust hole is closed and opened with the head, and the tail can be used to effectively form the arrangement of accommodating elastic components in the accommodating cavity therein, and by using the first flow groove between the head and the tail, the external exhaust pressure can be effectively introduced from the axial exhaust hole, and through the second flow groove communicated with the first flow groove,
  • the exhausted high-pressure gas is introduced into the accommodating cavity, so as to use the exhaust pressure and the elastic force of the elastic component to act together on the inner side of the head of the valve block, and the internal pressure of the compression cavity acts on the other side of the head of the valve block, It is necessary to make the internal pressure of the compression chamber greater than the exhaust pressure + elastic force to drive the valve block to move and open the exhaust channel; otherwise, the exhaust channel is closed to provide conditions for the automatic control of the exhaust valve assembly.
  • the number of the exhaust valve assemblies 7 is equal to the number of the sliding sheets 4 , or is an integer multiple of the number of the sliding sheets 4 .
  • the valve block 71 has a cylindrical structure
  • the first flow groove 713 is an annular groove opened along the circumference of the cylinder
  • the second flow groove 714 is formed at the tail portion 712 along the axial direction of the cylinder.
  • a strip groove is formed on the outer peripheral surface
  • the second flow groove 714 communicates with the accommodating cavity 710 at the end away from the annular groove.
  • At least two second flow grooves 714 are arranged at intervals along the circumference of the cylinder. This is a further optional structural form of the second flow groove of the present disclosure, and the area where the exhaust gas is introduced can be increased by a plurality of second flow grooves, and the automatic control capability can be improved.
  • An inserting groove 111 is formed on the end surface of the convex portion 11 , the thickness of the inserting groove 111 is adapted to the thickness of the baffle plate 73 , and the baffle plate 73 is inserted into the convex portion 11 from the inserting groove 111 .
  • the baffle plate 73 is used to cooperate with the valve block 71 , and the sealing effect of the exhaust valve assembly 7 can be ensured by the way that the baffle plate 73 and the valve block 71 are surface-fitted.
  • the thickness of the baffle 73 and the insert groove 111 is matched, so that a sealing fit is formed between the baffle 73 and the insert groove 111, so as to ensure the sealing effect between the baffle 73 and related components, thereby ensuring the working performance of the compressor.
  • the baffle 73 and the inserting groove 111 may be an interference fit, or may be fixed in the inserting groove 111 by means of gluing, so as to ensure the stability and reliability of the mounting structure of the baffle 73 .
  • the thickness B of the baffle 73 satisfies 1 ⁇ B ⁇ 5mm, so that the strength and installation space requirements of the baffle 73 can be well met.
  • the inserting groove 111 is parallel to the central axis of the main shaft 1 , and the inserting groove 111 is perpendicular to the central axis of the radial exhaust hole 51 .
  • valve port 731 is a circular hole with a radius of R2, the radial exhaust hole 51 has a radius of R1, and the valve block 71 is cylindrical with a radius of R3, where R2 ⁇ R3 ⁇ R1, in some embodiments , R3 ⁇ R1.
  • R3-R2 ⁇ 1mm so as to meet the assembly requirements of the valve block 71 and the matching requirements of the baffle plate 73 and the valve port 731 .
  • Figure 1 is a schematic diagram of the explosion of the pump body of the proposed solution, which is mainly composed of an upper flange, a lower flange, a cylinder, a main shaft, a sliding vane, a cover plate and a valve assembly (valve body, blocking column, spring).
  • 2 and 3 are a top view and a cross-sectional view of the pump body of the application solution, respectively.
  • Figure 6 is a diagram of the upper flange of the application scheme. The end face of the upper flange is provided with an arc-shaped exhaust groove, and at the same time, a number of exhaust ports are opened in the exhaust groove that communicate with the housing cavity.
  • Figure 7 is a diagram of the main shaft of the solution of the application.
  • FIG 8 is the valve block diagram of the application scheme.
  • the valve block is divided into a head and a tail.
  • the tail of the valve block is provided with a flow groove and a spring hole for assembling a spring.
  • Figure 9 is the block diagram of the application scheme, the block diameter B satisfies the relationship: 1mm ⁇ B ⁇ 5mm.
  • Figure 10 is a schematic diagram of the valve assembly and the main shaft after assembly.
  • At least one sliding vane slot 12 is further opened on the convex portion 11 , the sliding vane 4 is arranged in the sliding vane slot 12 , and the main shaft exhaust port 5 is arranged on the sliding vane slot 12 relatively close to compression in the circumferential direction.
  • the position of the end end (relative to the compressed suction end).
  • the main shaft exhaust port 5 is arranged at a position between two adjacent sliding vane grooves 12 in the circumferential direction, and the main shaft exhaust port 5 is relatively close to the compression position. The position of the slider groove 12 at the end.
  • two sliding vane grooves can also be arranged between two
  • spindle exhaust ports and the spindle exhaust port is set close to the sliding vane groove at the end of the compression, which can effectively reduce the clearance volume between the spindle exhaust port and the sliding vane in the compression chamber and improve the compression efficiency.
  • the flange exhaust port 6 includes a flange exhaust slot 61 and a flange exhaust hole 62 , and the flange exhaust slot 61 is provided on the flange 3 connected to the convex portion 11 .
  • One end face of the axial direction is opened along the axial direction
  • the flange exhaust hole 62 is arranged on the other axial end face of the flange 3 opposite to the convex portion 11 and opened along the axial direction
  • the flange exhaust groove 61 is opened in the axial direction.
  • the flange exhaust port of the present disclosure is communicated with the flange exhaust hole 62, and the other end of the flange exhaust slot 61 can be communicated with the main shaft exhaust port 5 during the rotation of the main shaft 1.
  • the flange exhaust groove provided on the axial end face in contact with the convex portion can be communicated with one or more main shaft exhaust grooves respectively, and through The flange exhaust hole on the other end face is used for exhaust.
  • the structure of the flange exhaust groove can ensure the communication with the main shaft exhaust port to the greatest extent, and prevent the main shaft exhaust port from being unable to communicate with the exhaust gas when it needs to be exhausted.
  • the structural strength and rigidity of the flange can be increased, and the exhaust requirements can be met at the same time.
  • the flange exhaust slot 61 is an arc-shaped slot extending in the circumferential direction
  • the flange exhaust hole 62 is at least one
  • the at least one flange exhaust hole 62 communicates with the flange exhaust slot 61 .
  • This is a further optional structural form of the flange exhaust groove and flange exhaust hole of the present disclosure.
  • the circumferentially extending arc groove structure can further ensure the communication function with multiple main shaft exhaust ports and ensure effective exhaust According to the requirement, at least one flange exhaust hole can be communicated with the flange exhaust groove to meet the exhaust requirements, and at the same time, the structural strength and rigidity of the flange can be improved (it is not necessary to provide a through groove).
  • the initial angle of the flange exhaust groove 61 is ⁇
  • the suction end angle of the pump body cavity of the compressor is ⁇ , and satisfies: ⁇ .
  • the initial angle ⁇ of the flange exhaust groove and the suction end angle ⁇ of the compressor pump body cavity satisfy: ⁇ .
  • the separation angle between the flange exhaust groove and the main shaft exhaust port is located after the tangent position between the main shaft and the inner diameter of the cylinder.
  • the flange 3 includes an upper flange 31 and a lower flange 32, and the upper flange 31 is provided with a flange exhaust port 6 and/or the lower flange 32 is provided with a flange exhaust port 6;
  • the exhaust valve assembly 7 when the pressure in the compression chamber 100 is greater than or equal to the preset exhaust pressure, the exhaust valve assembly 7 is opened to exhaust, and when the pressure in the compression chamber 100 is less than the preset exhaust pressure, the exhaust valve assembly 7 is opened. 7 close without venting;
  • the compressor is a vane compressor.
  • the flange is provided with flange exhaust grooves and flange exhaust holes (corresponding to the radial exhaust holes and axial ports of the main shaft). Flange exhaust grooves and flange exhaust holes are arranged on the upper part. With reference to Figure 12 and Figure 13, the flange exhaust holes are arranged in the flange exhaust groove, the number is not limited, and the flange exhaust groove and the outside of the pump body are connected.
  • the valve block 71 when the valve block 71 includes the first flow groove 713 and the second flow groove 714, the head 711 is subjected to the pressure P in the compression chamber 100 introduced by the radial exhaust hole 51, and the elastic member 72 is applied to the valve
  • the elastic force on the block 71 is F
  • the exhaust pressure introduced into the accommodating cavity 710 from the outside of the axial exhaust hole 52 through the first flow groove and the second flow groove is Pd
  • the exhaust valve assembly 7 is opened for exhausting
  • FIG. 2 is used to introduce the implementation process of the application solution.
  • the high pressure at the front end of the valve body will push the valve body to move backwards along the radial hole, so that the valve body is separated from the blocking column, that is, the valve assembly is in the open state, thus forming a Exhaust passage, so that the high pressure in the cavity reaches the compressor housing cavity through the main shaft radial exhaust hole-spindle axial exhaust hole-flange exhaust groove-flange exhaust port to complete the exhaust.
  • the present disclosure also provides an air conditioner including the compressor of any preceding item.
  • the exhaust methods of the present disclosure all adopt the structure design of main shaft exhaust port + exhaust valve + flange exhaust groove + flange exhaust hole, the main shaft is provided with an exhaust port, an exhaust valve is installed, and the flange is provided with an exhaust port.

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Abstract

一种压缩机，包括：主轴（1）、气缸（2）、法兰（3）和滑片（4），主轴（1）包括凸部（11），凸部（11）、气缸（2）、法兰（3）和滑片（4）共同形成压缩腔（100），凸部（11）上与每个压缩腔（100）对应地均开设有至少一个主轴排气口（5），法兰（3）上设置有法兰排气口（6），每个主轴排气口（5）的一端与压缩腔（100）连通，另一端能够在主轴（1）旋转的过程中与法兰排气口（6）连通、以进行排气，且在主轴排气口（5）中设置有排气阀组件（7），排气阀组件（7）包括挡板（73）、阀块（71）和弹性部件（72），挡板（73）从凸部（11）的端面嵌入径向排气孔（51）内，排气阀组件（7）能够根据压缩腔（100）内的压力大小进行自动排气。以及包括这种压缩机的空调器，这种压缩机的结构设计，有效保证每个压缩腔内排气口数量和面积固定，能够在满足压缩机排气速度要求的同时，保证压缩机在所有工况条件下均正常运行，排气速度连续变化。

Description

压缩机和空调器
本申请是以中国申请号为202010728357.7，申请日为2020年7月24日的申请为基础，并主张其优先权，该中国申请的公开内容在此作为整体引入本申请中。
技术领域
本公开涉及压缩机技术领域，具体涉及一种压缩机和空调器。
背景技术
专利号为201510044276.4的专利公开了一种压缩机排气结构，通过主轴上开设排气通道30与法兰上开设的导流通道20连通，实现压缩机末端排气。主要排气通过法兰上的排气口10实现。
专利号为201710916718.9的专利提出了一种压缩机结构，其中涉及到的主要排气口采用了和专利201510044276.4相同的原理，为了保证压缩机的排气口面积尽量大，减小排气损失，要求滑片扫过排气口时必须完全覆盖排气口，因此排气口增加大时需要采用菱形排气口结构。
但是上述2个专利方案存在以下问题：
1、主轴上排气通道30与法兰上导流通道20形成的排气通道，由于没有排气阀片，随着泵体转动，当主轴上排气通道30与法兰上导流通道20连通，则该排气通道打开，即为定压比设计，为了满足现有空调所有的使用，该设计压比要大于压缩机运行的所有工况压比，否则会出现部分工况欠压缩状态(未达到排气压力开始排气问题)，则设计要求该连通角度越靠后越好，该排气通道仅起到辅助排气的效果，利用率不高。
2、在压缩机排量较大时，为了增加大排气口面积，减小排气损失，出了法兰上的排气口采用菱形结构外，还需要增加排气口数量，则排气阀片组件数量同样增加，增加了压缩机零件数量，提高成本及可靠性隐患；同时在法兰上开设排气口结构，减小了法兰刚度，可能出现磨损及可靠性问题；另外由于排气口位置固定，当腔体经过某一法兰(菱形)排气口后，排气后关闭，则排气口面积突变，导致压缩机排气速度发生突变，对压缩机可靠性存在较大隐患。
3、滑片扫过法兰排气口时，排气口余隙容积的再膨胀引起的重复压缩，引起压缩机能效降低。
4、滑片扫过法兰排气口时，排气口气流可能对滑片运行产生影响，导致滑片发生倾 斜或受力发生变化引起的不稳定状态，影响压缩机可靠性。
5、压缩机每旋转一周，排气阀片打开N次(N为滑片数量)，阀片高频运行容易发生断裂等可靠性问题。
由于发明人了解的技术中的压缩机的排气口设置在法兰上、并与压缩腔相对，当腔体经过某一法兰排气口后，排气后关闭，则排气口面积突变，导致压缩机排气速度发生突变，对压缩机可靠性存在较大隐患的问题，本公开研究设计出一种压缩机和空调器。
发明内容
因此，本公开要解决的技术问题在于克服发明人了解的技术中的压缩机存在排气口面积突变，导致压缩机排气速度发生突变的缺陷，从而提供一种压缩机和空调器。
为了解决上述问题，本公开提供一种压缩机，其包括：
主轴、气缸、法兰和滑片，主轴包括凸部，凸部、气缸、法兰和滑片共同形成压缩腔，凸部上与每个压缩腔对应地均开设有至少一个主轴排气口，法兰上设置有法兰排气口，每个主轴排气口的一端与压缩腔连通，另一端能够在主轴旋转的过程中与法兰排气口连通、以进行排气，且在主轴排气口中设置有排气阀组件，排气阀组件能够根据压缩腔内的压力大小进行自动排气；
主轴排气口包括径向排气孔和轴向排气孔，径向排气孔开设在凸部的径向外侧面并沿径向方向开设，轴向排气孔开设在凸部的轴向端面并沿轴向方向开设，轴向排气孔与径向排气孔连通，使得气流从压缩腔、径向排气孔和轴向排气孔依次通过；
排气阀组件包括挡板、阀块和弹性部件，挡板从凸部的端面嵌入径向排气孔内，阀块和弹性部件设置于径向排气孔中，阀块的一端内部形成有容纳腔、以容纳弹性部件的至少部分设置于其中，阀块的另一端与挡板相对设置，挡板上设置有阀口，阀块能够做往复运动打开或者关闭阀口，使得压缩腔与轴向排气孔在连通和关闭连通之间切换。
在一些实施例中，阀块包括头部和尾部，头部与挡板相对设置，头部和尾部相接的位置形成有环形的第一流通槽，第一流通槽能够与轴向排气孔相连通以从轴向排气孔处引入排气压力，尾部开设有第二流通槽，第二流通槽的一端与第一流通槽连通、另一端与容纳腔连通，容纳腔形成于尾部的内部。
在一些实施例中，阀块为圆柱体结构，第一流通槽为沿圆柱体的周向开设的圆环形凹槽，第二流通槽为沿圆柱体的轴向在尾部的外周面上开设的条形槽，第二流通槽在远离所述圆环形凹槽的末端与容纳腔连通。
在一些实施例中，第二流通槽为至少两个、且沿圆柱体的周向间隔排布设置。
在一些实施例中，凸部的端面上开设有嵌槽，嵌槽的厚度与挡板的厚度相适配，挡板从嵌槽卡入凸部内。
在一些实施例中，挡板的厚度B满足1≤B≤5mm。
在一些实施例中，嵌槽与主轴的中心轴线相平行，且嵌槽垂直于径向排气孔的中心轴线。
在一些实施例中，径向排气孔为至少两个、且沿主轴的轴线方向间隔设置，每个径向排气孔内均设置有排气阀组件；和/或，轴向排气孔沿主轴的轴线方向贯穿凸部的上下端面。
在一些实施例中，凸部上还开设有至少一个滑片槽，滑片设置于滑片槽中，主轴排气口设置在滑片槽的沿圆周方向的相对靠近压缩结束端的位置。
在一些实施例中，当滑片槽为两个以上时，主轴排气口设置在两个相邻滑片槽沿周向之间的位置，且主轴排气口相对地靠近位于压缩结束端的滑片槽的位置。
在一些实施例中，法兰排气口包括法兰排气槽和法兰排气孔，法兰排气槽设置于法兰的与凸部相接的轴向一端面上且沿轴向方向开设，法兰排气孔设置于法兰的与凸部相背的轴向另一端面上且沿轴向方向开设，法兰排气槽的一端与法兰排气孔连通，法兰排气槽的另一端能在主轴转动过程中与主轴排气口连通。
在一些实施例中，法兰排气槽为沿周向延伸的弧形槽，法兰排气孔为至少一个，且至少一个法兰排气孔与法兰排气槽连通。
在一些实施例中，法兰排气槽的起始角度为β，压缩机的泵体腔体吸气结束角度为α，并满足：α≥β。
在一些实施例中，法兰包括上法兰和下法兰，上法兰上开设有法兰排气口和/或下法兰上开设有法兰排气口；
和/或，当压缩腔内的压力大于等于预设排气压力时，排气阀组件打开而进行排气，当压缩腔内的压力小于预设排气压力时，排气阀组件关闭而不进行排气；
和/或，压缩机为滑片式压缩机。
在一些实施例中，当阀块包括第一流通槽和第二流通槽时，头部承受径向排气孔引入的压缩腔中的压力P，弹性部件施加到阀块上的弹性力为F，通过第一流通槽和第二流通槽从轴向排气孔外部引入至容纳腔中的排气压力为Pd，当P*S1＞Pd*S2+F，排气阀组件打开而进行排气，当P*S1＜Pd*S2+F时，排气阀组件关闭而不进行排气，其中S1为径向排气孔的面积，S2为阀块的面积。
本公开还提供一种空调器，其包括前任一项的压缩机。
本公开提供的一种压缩机和空调器具有如下有益效果之一：
本公开通过将排气口设置在主轴的凸部上、有效的取消掉现有在法兰上与压缩腔对应的位置设置的排气结构，由于凸部随着主轴一同转动、从而使得主轴排气口始终位于两个滑片之间的位置，并且通过排气阀组件设置于主轴排气口内部能够根据压缩腔内的大小 而进行自动开启排气阀组件而进行排气或关闭排气，当所述压缩腔内的压力大于等于预设排气压力时，所述排气阀组件打开而进行排气，当所述压缩腔内的压力小于预设排气压力时，所述排气阀组件关闭而不进行排气；即采用主轴排气口+排气阀组件+法兰排气口的结构设计，有效保证每个压缩腔内排气口数量和面积固定，能够在满足压缩机排气速度要求的同时，保证压缩机在所有工况条件下均正常运行，排气速度连续变化；
本公开并且由于不需再从与压缩腔相对的法兰排气口处进行排气，有效地避免了原法兰排气口余隙容积膨胀引起的再压缩引起的功耗大问题，提高压缩机了能效；原有与压缩腔对应的法兰排气口在排气时会对滑片的头部产生气流影响，本申请通过在主轴的凸部上设置主轴排气口，使得时滑片运动不再受法兰排气口气流的影响，保证压缩机可靠性；本申请的压缩机旋转一周，阀块打开一次，提高阀块可靠性，有效解决发明人了解的技术中压缩机每旋转一周，排气阀片打开N次(N为滑片数量)，阀片高频运行容易发生断裂等可靠性问题。
附图说明
图1是本公开的压缩机泵体部分的分解结构图；
图2是本公开的压缩机泵体部分的俯视图；
图3是本公开的压缩机吸气/压缩阶段泵体剖视图；
图4是本公开的吸气/压缩阶段排气口位置剖视局部放大图(图3的A部分的局部放大图，图2中位置1，阀块未打开)；
图5是本公开的排气阶段排气口位置剖视局部放大图(图3的A部分的局部放大图，图2中位置2，阀块打开)；
图6是本公开的上法兰的立体、俯视、仰视以及A-A剖视图；
图7是本公开的压缩机的主轴的立体、正视、俯视和B部分的放大图；
图8是本公开的压缩机的阀块的立体、正视和纵剖视结构图；
图9是本公开的压缩机的挡柱的立体和正视结构图；
图10是本公开的压缩机的主轴与阀组件装配的立体、正面剖视和俯视图；
附图标记表示为：
1、主轴；11、凸部；111、挡柱槽；12、滑片槽；100、压缩腔；2、气缸；3、法兰；31、上法兰；32、下法兰；4、滑片；5、主轴排气口；51、径向排气孔；52、轴向排气孔；6、法兰排气口；61、法兰排气槽；62、法兰排气孔；7、排气阀组件；71、阀块；710、容纳腔；711、头部；712、尾部；713、第一流通槽；714、第二流通槽；72、弹性部件；73、阻挡部件；731、阻挡部件；8、盖板。
具体实施方式
如图1-10所示，本公开提供一种压缩机，其包括：
主轴1、气缸2、法兰3和滑片4，主轴1包括凸部11，凸部11、气缸2、法兰3和滑片4共同形成压缩腔100，凸部11上与每个压缩腔100对应地均开设有至少一个主轴排气口5，法兰3上设置有法兰排气口6，(可选地，法兰排气口在径向方向上与主轴排气口相对设置，能够在径向方向保证法兰排气口和主轴排气口连通)，每个主轴排气口5的一端与压缩腔100连通，另一端能够在主轴旋转的过程中与法兰排气口6连通、以进行排气，且在主轴排气口5中设置有排气阀组件7，排气阀组件7能够根据压缩腔100内的压力大小进行自动排气；
主轴排气口5包括径向排气孔51和轴向排气孔52，径向排气孔51开设在凸部11的径向外侧面并沿径向方向开设，轴向排气孔52开设在凸部11的轴向端面并沿轴向方向开设，轴向排气孔52与径向排气孔51连通，使得气流从压缩腔100、径向排气孔51和轴向排气孔52依次通过；
排气阀组件7包括挡板73、阀块71和弹性部件72(可选地，弹簧)，挡板73从凸部11的端面嵌入径向排气孔51内，阀块71和弹性部件72设置于径向排气孔51中，阀块71的一端内部形成有容纳腔710、以容纳弹性部件72的至少部分设置于其中，阀块71的另一端与挡板73相对设置，挡板73上设置有阀口731，阀块71能够做往复运动打开或者关闭阀口731，使得压缩腔100与轴向排气孔52在连通和关闭连通之间切换。
本公开通过将排气口设置在主轴的凸部上、有效的取消掉现有在法兰上与压缩腔对应的位置设置的排气结构，由于凸部随着主轴一同转动、从而使得主轴排气口始终位于两个滑片之间的位置，并且通过排气阀组件设置于主轴排气口内部能够根据压缩腔内的大小而进行自动开启排气阀组件而进行排气或关闭排气，当压缩腔100内的压力大于等于预设排气压力时，排气阀组件7打开而进行排气，当压缩腔100内的压力小于预设排气压力时，排气阀组件7关闭而不进行排气；即采用主轴排气口+排气阀组件+法兰排气口的结构设计，有效保证每个压缩腔内排气口数量和面积固定，能够在满足压缩机排气速度要求的同时，保证压缩机在所有工况条件下均正常运行，排气速度连续变化。
本公开的主轴排气口包括径向排气孔、能够通过径向排气孔从压缩腔中连通并引入气体，轴向排气孔用于将径向排气孔过来的气体连通并导入至法兰排气口中、进行有效排气，有效地替换并取消了发明人了解的技术中采用法兰上与压缩腔位置相对设置排气口的结构，有效保证每个压缩腔内排气口数量和面积固定，排气速度连续变化。
本公开通过挡板、阀块和弹性部件相配合形成排气阀结构，能够利用弹性部件的弹 性力将阀块的初始状态抵接到径向排气孔处以在压缩腔中压力较小时关闭排气(如图4)，但当压缩腔中压力高于预设排气压力时、压力克服弹性压力和轴向排气孔中引入的排气端的高压的和值，推动阀块朝远离径向排气孔的方向运动，打开径向排气孔，使得径向排气孔与轴向排气孔连通，以使得压力大于预设排气压力值时自动排气，压力小于预设排气压力值时关闭自动排气(如图4-5)。
由于挡板73上开设有阀口731，且挡板73从凸部11的端面嵌入到凸部11内，并且位于径向排气孔51的路径上，通过阀口731使得挡板73两端的径向排气孔51连通。该种结构使得挡板73从径向排气孔51的侧部插入到径向排气孔51内，能够利用挡板73对阀块71形成止挡，无需利用径向排气孔51自身的结构来对阀块71形成止挡，因此可以方便径向排气孔51的设置，使得阀块71可以直接从径向排气孔51的进口处装入到径向排气孔51内，降低了阀块71的安装难度，使得排气阀组件7的安装更加简单方便。挡板73与阀块71之间在阀口731处能够实现面接触，从而能够提高排气阀组件7的整体密封性能，提高排气阀组件7的工作性能。
本公开并且由于不需再从与压缩腔相对的法兰排气口处进行排气，有效地避免了原法兰排气口余隙容积膨胀引起的再压缩引起的功耗大问题，提高压缩机了能效；原有与压缩腔对应的法兰排气口在排气时会对滑片的头部产生气流影响，本申请通过在主轴的凸部上设置主轴排气口，使得时滑片运动不再受法兰排气口气流的影响，保证压缩机可靠性；本申请的压缩机旋转一周，阀块打开一次，提高阀块可靠性，有效解决发明人了解的技术中压缩机每旋转一周，排气阀片打开N次(N为滑片数量)，阀片高频运行容易发生断裂等可靠性问题。
本公开的主轴上设置有排气口，安装有排气阀组件，法兰上设置有法兰排气槽和法兰排气孔，当压缩腔腔体压力高于泵体外部排气压力和阀弹簧的弹簧力的综合作用力时，阀块沿径向排气孔移动，腔体通过主轴排气口与法兰排气槽连通，并通过法兰排气孔排出压缩机泵体，实现压缩机排气。保证每个压缩腔内排气口数量和面积固定，满足压缩机排气速度要求的同时，保证压缩机在所有工况条件下均正常运行，排气速度连续变化，避免原法兰排气口余隙容积膨胀引起的再压缩引起的功耗大问题，提高压缩机了能效。同时滑片运动不受法兰排气口气流的影响，保证压缩机可靠性。
在一些实施例中，阀块71包括头部711和尾部712，头部711与挡板73相对设置，头部711和尾部712相接的位置形成有环形的第一流通槽713，第一流通槽713能够与轴向排气孔52相连通以从轴向排气孔52处引入排气压力，尾部712的外周面上开设有第二流通槽714，第二流通槽714的一端与第一流通槽713连通、另一端与容纳腔710连通，容纳腔710形成于尾部712的内部。这是本公开的阀块的可选结构形式，即通过头部和尾部的结构形式，利用头部而对径向排气孔的端部进行封闭和打开、利用尾部能够有效形成 容纳弹性部件设置于其中的容纳腔，并且利用头部和尾部之间的第一流通槽、能够有效从轴向排气孔处引入外部的排气压力、并通过与第一流通槽连通的第二流通槽，将排气的高压气体引入容纳腔中，以利用排气压力和弹性部件的弹性力共同作用于阀块的头部的内侧，压缩腔的内部压力作用于阀块的头部的另一侧，需要使得压缩腔内部压力大于排气压力+弹性力时才能驱动阀块运动、打开排气通道，否则则关闭排气通道，为排气阀组件的自动控制提供条件。
在一些实施例中，排气阀组件7的数量与滑片4的数量相等，或者为滑片4数量的整数倍。
在一些实施例中，阀块71为圆柱体结构，第一流通槽713为沿圆柱体的周向开设的圆环形凹槽，第二流通槽714为沿圆柱体的轴向在尾部712的外周面上开设的条形槽，第二流通槽714在远离圆环形凹槽的末端与容纳腔710连通。这是本公开的阀块的进一步可选结构形式，即采用圆柱体结构的阀块能够有效地设置于径向排气孔中，圆弧形凹槽用于引入外部气体、第二流通槽形成为条形槽，将气体从第一流通槽导入至径向内部的容纳腔中。
在一些实施例中，第二流通槽714为至少两个、且沿圆柱体的周向间隔排布设置。这是本公开的第二流通槽的进一步可选结构形式，通过多个的第二流通槽能够增大引入排气气体的面积，提高自动控制的能力。
凸部11的端面上开设有嵌槽111，嵌槽111的厚度与挡板73的厚度相适配，挡板73从嵌槽111卡入凸部11内。在本实施例中，采用挡板73来与阀块71进行配合，可以利用挡板73与阀块71面配合的方式来保证排气阀组件7的密封效果。而挡板73与嵌槽111的厚度相适配，使得挡板73与嵌槽111之间形成密封配合，保证挡板73与相关部件之间的密封效果，进而保证压缩机的工作性能。挡板73与嵌槽111之间可以为过盈配合，也可以通过胶粘固定的方式固定在嵌槽111内，从而保证挡板73安装结构的稳定性和可靠性。
挡板73的厚度B满足1≤B≤5mm，从而能够很好地满足挡板73的强度和装配空间要求。
嵌槽111与主轴1的中心轴线相平行，且嵌槽111垂直于径向排气孔51的中心轴线。
在本实施例中，阀口731为圆孔，半径为R2，径向排气孔51的半径为R1，阀块71为圆柱形，半径为R3，其中R2＜R3≤R1，在一些实施例中，R3＜R1。
在一些实施例中，R3-R2≥1mm，从而能够满足阀块71的装配要求，以及挡板73与阀口731的配合要求。
在弹簧装配后，在排气阀处于关闭状态时，其压缩量L和刚度K满足关系式：1N≤KL≤10N，以保证压缩机排气顺畅。
如图1为所申请方案泵体爆炸示意图，其主要由上法兰、下法兰、气缸、主轴、滑片、盖板及阀组件(阀体、挡柱、弹簧)组成。图2和3分别为申请方案泵体俯视图和截面图。图6为申请方案上法兰图，上法兰端面开设有弧形排气槽，同时在排气槽内开设有若干与壳体腔连通的排气口。如图7为本申请方案主轴图，主轴中心部上、下端面开设有排气孔和挡柱槽，排气孔由平行于主轴轴心的轴向排气孔和垂直于轴心的径向排气孔组成，挡柱槽与轴心平行，并垂直于主轴径向排气孔。如图8为申请方案阀块图，阀块分为头部和尾部，阀块尾部开设有流通槽和用来装配弹簧的弹簧孔。如图9为申请方案挡柱图，挡柱直径B满足关系：1mm≤B≤5mm。如图10为阀组件与主轴装配后的示意图。
在一些实施例中，径向排气孔51为至少两个、且沿主轴的轴线方向间隔设置；和/或，轴向排气孔52沿主轴的轴线方向贯穿凸部11的上下端面。这是本公开的可选结构形式，径向排气孔为多个、图中显示为沿轴向并排排布的2个，能够通过多个径向排气孔同时排气，增大排气面积，提高排气速度，轴向排气孔贯穿凸部的上下端面能够保证每个径向排气孔都可以连通到法兰排气槽和排气口，增强排气效果。
在一些实施例中，凸部11上还开设有至少一个滑片槽12，滑片4设置于滑片槽12中，主轴排气口5设置在滑片槽12的沿圆周方向的相对靠近压缩结束端的位置(相对于压缩吸气端)。进一步在一些实施例中，当滑片槽12为两个以上时，主轴排气口5设置在两个相邻滑片槽12沿周向之间的位置，且主轴排气口5相对地靠近位于压缩结束端的滑片槽12的位置。这是本公开的滑片槽和主轴排气口的可选结构关系，即可选形式为两个滑片槽周向之间设置一个主轴排气口，当然两个滑片槽之间还可以设置两个以上或多个的主轴排气口，主轴排气口靠近压缩结束端的滑片槽设置，这样能够有效降低压缩腔内存在于主轴排气口和滑片之间的余隙容积，提高压缩效率。
如图5，在一些实施例中，法兰排气口6包括法兰排气槽61和法兰排气孔62，法兰排气槽61设置于法兰3的与凸部11相接的轴向一端面上且沿轴向方向开设，法兰排气孔62设置于法兰3的与凸部11相背的轴向另一端面上且沿轴向方向开设，法兰排气槽61的一端与法兰排气孔62连通，法兰排气槽61的另一端能在主轴1转动过程中与主轴排气口5连通。这是本公开的法兰排气口的可选结构形式，即通过与凸部相接轴向端面设置的法兰排气槽能够与一个或多个的主轴排气槽进行分别连通，并通过另一端面处的法兰排气孔进行排出，通过法兰排气槽的结构能够最大限度地保证与主轴排气口的连通作用，防止主轴排气口在需要排气的时候无法连通排出气体，并且通过另一端面设置的间隔设置的法兰排气孔，能够增大法兰的结构强度和刚度，同时满足排气需求。
在一些实施例中，法兰排气槽61为沿周向延伸的弧形槽，法兰排气孔62为至少一个，且至少一个法兰排气孔62与法兰排气槽61连通。这是本公开的法兰排气槽和法兰排气孔的进一步可选结构形式，周向延伸的弧形槽结构能够进一步保证与多个主轴排气口的 连通作用，保证有效的排气需求，至少一个法兰排气孔能够在通过与法兰排气槽连通以满足排气的同时还能提高法兰的结构强度和刚度(不必开设通槽)。
在一些实施例中，法兰排气槽61的起始角度为β，压缩机的泵体腔体吸气结束角度为α，并满足：α≥β。通过这样的结构设置能够有效保证在进入压缩段的压缩腔中的主轴排气口均能连通至法兰排气槽，防止存在部分压缩腔中的主轴排气口位置无法连通至法兰排气槽中的情况、避免无法满足所有工况情况，实现所有工况(不同压比)均能达到的效果。
为了满足所有工况(不同压比，特别是压比为1时)的使用，法兰排气槽起始角度β与压缩机泵体腔体吸气结束角度α，满足：α≥β。同时，为了保证其他的完全排出，法兰排气槽与主轴排气口脱离角度位于主轴和气缸内径相切位置之后。
在一些实施例中，法兰3包括上法兰31和下法兰32，上法兰31上开设有法兰排气口6和/或下法兰32上开设有法兰排气口6；
和/或，当压缩腔100内的压力大于等于预设排气压力时，排气阀组件7打开而进行排气，当压缩腔100内的压力小于预设排气压力时，排气阀组件7关闭而不进行排气；
和/或，压缩机为滑片式压缩机。
这是本公开的法兰的可选结构形式，通过在上下法兰上均设置法兰排气口能够增大排气面积，提高排气效果，根据需求，可以在仅在上法兰或下法兰设置法兰排气槽和法兰排气孔(对应主轴径向排气孔和轴向口)，当受结构限制，排气口面积不足时，可以同时在上法兰和下法兰上设置法兰排气槽和法兰排气孔。结合图12和图13，法兰排气孔设置法兰排气槽中，数量不限，连通法兰排气槽和泵体外部。当压缩机排气时，气流先经过主轴排气口，打开排气阀块，进入法兰排气槽，再经过法兰排气孔排出泵体。
本公开通过压缩腔100内的压力大于等于预设排气压力(预设排气压力＝弹性部件的预设弹性力+排气腔的排气压力)时，排气阀组件7打开而进行排气，当压缩腔100内的压力小于预设排气压力时，排气阀组件7关闭而不进行排气，能够实现根据压缩腔内的压力通过排气阀组件进行自动排气。
在一些实施例中，当阀块71包括第一流通槽713和第二流通槽714时，头部711承受径向排气孔51引入的压缩腔100中的压力P，弹性部件72施加到阀块71上的弹性力为F，通过第一流通槽和第二流通槽从轴向排气孔52外部引入至容纳腔710中的排气压力为Pd，当P*S1＞Pd*S2+F，排气阀组件7打开而进行排气，当P*S1＜Pd*S2+F时，排气阀组件7关闭而不进行排气，其中S1为径向排气孔的面积，S1＝πR1 2，R1为径向排气孔的半径，S2为阀块的面积，S1＝(πR2 2)/4，R2为阀块的直径。
具体的，以图2来介绍申请方案实现过程。
当压缩机泵体运行至如图2所示时刻，位置1处一个主轴轴向排气孔刚好与法兰排 气副槽相连通，如图4，阀体受力为：前端受到腔体压力P1，后端受到弹簧力F和引入的高压产生的力Pd，且由于位置1还处于压缩阶段，因此P1＜Pd+F，阀体与挡柱处于紧密贴合状态，即阀组件关闭状态。与此同时，由于位置2处处于排气阶段，如图5，此时主轴径向排气孔-主轴轴向排气孔-法兰排气槽-法兰排气口-壳体腔彼此相连通，此时阀体前后端的受力关系为P2＞Pd+F，阀体前端的高压力会推动阀体沿径向孔向后运动，使阀体脱离挡柱，即阀组件开启状态，从而形成排气通道，以使腔内高压通过主轴径向排气孔-主轴轴向排气孔-法兰排气槽-法兰排气口到达压缩机壳体腔，完成排气。
本公开还提供一种空调器，其包括前任一项的压缩机。本公开的排气方式全部采用主轴排气口+排气阀+法兰排气槽+法兰排气孔的结构设计，主轴上设置有排气口，安装有排气阀，法兰上设置有法兰排气槽和法兰排气孔，当压缩腔腔体压力高于泵体外部排气压力和弹簧的弹簧力的综合作用力时，阀块沿径向排气孔方向移动，主轴径向排气孔和轴向排气孔连通，并与法兰排气槽连通，通过法兰排气孔排出压缩机泵体，实现压缩机排气。保证每个压缩腔内排气口数量和面积固定，满足压缩机排气速度要求的同时，保证压缩机在所有工况条件下均正常运行，排气速度连续变化，避免原法兰排气口余隙容积膨胀引起的再压缩引起的功耗大问题，提高压缩机了能效。同时滑片运动不受法兰排气口气流的影响，保证压缩机可靠性。
以上所述仅为本公开的较佳实施例而已，并不用以限制本公开，凡在本公开的精神和原则之内所作的任何修改、等同替换和改进等，均应包含在本公开的保护范围之内。以上所述仅是本公开的可选实施方式，应当指出，对于本技术领域的普通技术人员来说，在不脱离本公开技术原理的前提下，还可以做出若干改进和变型，这些改进和变型也应视为本公开的保护范围。

Claims (16)

  1. 一种压缩机，包括：
    主轴(1)、气缸(2)、法兰(3)和滑片(4)，所述主轴(1)包括凸部(11)，所述凸部(11)、所述气缸(2)、所述法兰(3)和所述滑片(4)共同形成压缩腔(100)，所述凸部(11)上与每个所述压缩腔(100)对应地均开设有至少一个主轴排气口(5)，所述法兰(3)上设置有法兰排气口(6)，每个所述主轴排气口(5)的一端与所述压缩腔(100)连通，另一端能够在主轴旋转的过程中与所述法兰排气口(6)连通、以进行排气，且在所述主轴排气口(5)中设置有排气阀组件(7)，所述排气阀组件(7)能够根据所述压缩腔(100)内的压力大小进行自动排气；
    所述主轴排气口(5)包括径向排气孔(51)和轴向排气孔(52)，所述径向排气孔(51)开设在所述凸部(11)的径向外侧面并沿径向方向开设，所述轴向排气孔(52)开设在所述凸部(11)的轴向端面并沿轴向方向开设，所述轴向排气孔(52)与所述径向排气孔(51)连通，使得气流从所述压缩腔(100)、所述径向排气孔(51)和所述轴向排气孔(52)依次通过；
    所述排气阀组件(7)包括挡板(73)、阀块(71)和弹性部件(72)，所述挡板(73)从所述凸部(11)的端面嵌入所述径向排气孔(51)内，所述阀块(71)和所述弹性部件(72)设置于所述径向排气孔(51)中，所述阀块(71)的一端内部形成有容纳腔(710)、以容纳所述弹性部件(72)的至少部分设置于其中，所述阀块(71)的另一端与所述挡板(73)相对设置，所述挡板(73)上设置有阀口(731)，所述阀块(71)能够做往复运动打开或者关闭所述阀口(731)，使得所述压缩腔(100)与所述轴向排气孔(52)在连通和关闭连通之间切换。
  2. 根据权利要求1所述的压缩机，其中：
    所述阀块(71)包括头部(711)和尾部(712)，所述头部(711)与所述挡板(73)相对设置，所述头部(711)和尾部(712)相接的位置形成有环形的第一流通槽(713)，所述第一流通槽(713)能够与所述轴向排气孔(52)相连通以从所述轴向排气孔(52)处引入排气压力，所述尾部(712)开设有第二流通槽(714)，所述第二流通槽(714)的一端与所述第一流通槽(713)连通、另一端与所述容纳腔(710)连通，所述容纳腔(710)形成于所述尾部(712)的内部。
  3. 根据权利要求2所述的压缩机，其中：
    所述阀块(71)为圆柱体结构，所述第一流通槽(713)为沿所述圆柱体的周向开设的圆环形凹槽，所述第二流通槽(714)为沿所述圆柱体的轴向在所述尾部(712)的外周面上开设的条形槽，所述第二流通槽(714)在远离所述圆环形凹槽的末端与所述容纳腔 (710)连通。
  4. 根据权利要求2或3所述的压缩机，其中：
    所述第二流通槽(714)为至少两个、且沿所述圆柱体的周向间隔排布设置。
  5. 根据权利要求1-4中任一所述的压缩机，其中：
    所述凸部(11)的端面上开设有嵌槽(111)，所述嵌槽(111)的厚度与所述挡板(73)的厚度相适配，所述挡板(73)从所述嵌槽(111)卡入所述凸部(11)内。
  6. 根据权利要求5所述的压缩机，其特征在于：
    所述挡板(73)的厚度B满足1≤B≤5mm。
  7. 根据权利要求5或6所述的压缩机，其中：
    所述嵌槽(111)与所述主轴(1)的中心轴线相平行，且所述嵌槽(111)垂直于所述径向排气孔(51)的中心轴线。
  8. 根据权利要求1-7中任一项所述的压缩机，其中：
    所述径向排气孔(51)为至少两个、且沿所述主轴的轴线方向间隔设置，每个所述径向排气孔(51)内均设置有所述排气阀组件(7)；和/或，所述轴向排气孔(52)沿所述主轴的轴线方向贯穿所述凸部(11)的上下端面。
  9. 根据权利要求1-8中任一项所述的压缩机，其中：
    所述凸部(11)上还开设有至少一个滑片槽(12)，所述滑片(4)设置于所述滑片槽(12)中，所述主轴排气口(5)设置在所述滑片槽(12)的沿圆周方向的相对靠近压缩结束端的位置。
  10. 根据权利要求9所述的压缩机，其中：
    当滑片槽(12)为两个以上时，所述主轴排气口(5)设置在两个相邻所述滑片槽(12)沿周向之间的位置，且所述主轴排气口(5)相对地靠近位于压缩结束端的滑片槽(12)的位置。
  11. 根据权利要求1-10中任一项所述的压缩机，其中：
    所述法兰排气口(6)包括法兰排气槽(61)和法兰排气孔(62)，所述法兰排气槽(61)设置于所述法兰(3)的与所述凸部(11)相接的轴向一端面上且沿轴向方向开设，所述法兰排气孔(62)设置于所述法兰(3)的与所述凸部(11)相背的轴向另一端面上且沿轴向方向开设，所述法兰排气槽(61)的一端与所述法兰排气孔(62)连通，所述法兰排气槽(61)的另一端能在所述主轴(1)转动过程中与所述主轴排气口(5)连通。
  12. 根据权利要求11所述的压缩机，其中：
    所述法兰排气槽(61)为沿周向延伸的弧形槽，所述法兰排气孔(62)为至少一个，且至少一个所述法兰排气孔(62)与所述法兰排气槽(61)连通。
  13. 根据权利要求12所述的压缩机，其中：
    所述法兰排气槽(61)的起始角度为β，所述压缩机的泵体腔体吸气结束角度为α，并满足：α≥β。
  14. 根据权利要求1-13中任一项所述的压缩机，其中：
    所述法兰(3)包括上法兰(31)和下法兰(32)，所述上法兰(31)上开设有所述法兰排气口(6)和/或所述下法兰(32)上开设有所述法兰排气口(6)；
    和/或，当所述压缩腔(100)内的压力大于等于预设排气压力时，所述排气阀组件(7)打开而进行排气，当所述压缩腔(100)内的压力小于预设排气压力时，所述排气阀组件(7)关闭而不进行排气；
    和/或，所述压缩机为滑片式压缩机。
  15. 根据权利要求1-14中任一所述的压缩机，其中：
    当所述阀块(71)包括第一流通槽(713)和第二流通槽(714)时，所述头部(711)承受所述径向排气孔(51)引入的所述压缩腔(100)中的压力P，所述弹性部件(72)施加到所述阀块(71)上的弹性力为F，通过所述第一流通槽和所述第二流通槽从所述轴向排气孔(52)外部引入至所述容纳腔(710)中的排气压力为Pd，当P*S1＞Pd*S2+F，所述排气阀组件(7)打开而进行排气，当P*S1＜Pd*S2+F时，所述排气阀组件(7)关闭而不进行排气，其中S1为径向排气孔的面积，S2为阀块的面积。
  16. 一种空调器，包括权利要求1-15中任一项所述的压缩机。
PCT/CN2021/089286 2020-07-24 2021-04-23 压缩机和空调器 Ceased WO2022016934A1 (zh)

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Publication number Priority date Publication date Assignee Title
CN112145417B (zh) * 2020-07-24 2023-04-28 珠海格力电器股份有限公司 一种压缩机和空调器
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CN116816683A (zh) * 2023-07-07 2023-09-29 广东美的环境科技有限公司 压缩机和制冷设备

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4373882A (en) * 1981-01-30 1983-02-15 General Electric Company Discharge valve assembly for compressor
CN1133400A (zh) * 1994-12-28 1996-10-16 东芝株式会社 回转式压缩机
CN102996457A (zh) * 2012-12-03 2013-03-27 珠海格力电器股份有限公司 旋转式压缩机及排气阀
KR20150083368A (ko) * 2014-01-09 2015-07-17 한라비스테온공조 주식회사 베인 로터리 압축기
CN105987004A (zh) * 2015-01-28 2016-10-05 珠海格力节能环保制冷技术研究中心有限公司 滑片式压缩机及其排气结构
CN111287962A (zh) * 2018-12-07 2020-06-16 Lg电子株式会社 旋转式压缩机
CN112145417A (zh) * 2020-07-24 2020-12-29 珠海格力电器股份有限公司 一种压缩机和空调器

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60206996A (ja) * 1984-03-31 1985-10-18 Shimadzu Corp 真空ポンプ
JP2013241851A (ja) * 2012-05-18 2013-12-05 Calsonic Kansei Corp 気体圧縮機
JP2014058891A (ja) * 2012-09-18 2014-04-03 Hitachi Automotive Systems Ltd ポンプ装置
CN105864037B (zh) * 2015-01-23 2018-10-02 珠海格力电器股份有限公司 泵体结构及压缩机
CN106151032A (zh) * 2015-03-31 2016-11-23 珠海格力节能环保制冷技术研究中心有限公司 滑片式压缩机及空调系统

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4373882A (en) * 1981-01-30 1983-02-15 General Electric Company Discharge valve assembly for compressor
CN1133400A (zh) * 1994-12-28 1996-10-16 东芝株式会社 回转式压缩机
CN102996457A (zh) * 2012-12-03 2013-03-27 珠海格力电器股份有限公司 旋转式压缩机及排气阀
KR20150083368A (ko) * 2014-01-09 2015-07-17 한라비스테온공조 주식회사 베인 로터리 압축기
CN105987004A (zh) * 2015-01-28 2016-10-05 珠海格力节能环保制冷技术研究中心有限公司 滑片式压缩机及其排气结构
CN111287962A (zh) * 2018-12-07 2020-06-16 Lg电子株式会社 旋转式压缩机
CN112145417A (zh) * 2020-07-24 2020-12-29 珠海格力电器股份有限公司 一种压缩机和空调器

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