CN111963435B - Compressor and air conditioner - Google Patents
Compressor and air conditioner Download PDFInfo
- Publication number
- CN111963435B CN111963435B CN202010728223.5A CN202010728223A CN111963435B CN 111963435 B CN111963435 B CN 111963435B CN 202010728223 A CN202010728223 A CN 202010728223A CN 111963435 B CN111963435 B CN 111963435B
- Authority
- CN
- China
- Prior art keywords
- exhaust
- flange
- exhaust port
- main shaft
- radial
- 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.)
- Active
Links
Images
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
Abstract
The invention provides a compressor and an air conditioner, the compressor includes: the main shaft, the cylinder, flange and gleitbretter, the main shaft includes the convex part, the cylinder, flange and gleitbretter form the compression chamber jointly, at least one main shaft gas vent has all been seted up with every compression chamber on the convex part correspondingly, be provided with the flange gas vent on the flange, the one end and the compression chamber intercommunication of every main shaft gas vent, the other end can communicate with the flange gas vent at the rotatory in-process of main shaft, in order to exhaust, and be provided with the exhaust valve subassembly in the main shaft gas vent, the exhaust valve subassembly can carry out self-bleeding according to the pressure size in the compression chamber. According to the invention, by adopting the structural design of the main shaft exhaust port, the exhaust valve assembly and the flange exhaust port, the quantity and area of the exhaust ports in each compression cavity are effectively ensured to be fixed, the exhaust speed requirement of the compressor can be met, and the compressor can be ensured to normally operate under all working conditions and the exhaust speed is continuously changed.
Description
Technical Field
The invention relates to the technical field of compressors, in particular to a compressor and an air conditioner.
Background
Patent No. 201510044276.4 discloses a compressor exhaust structure, which realizes the exhaust at the tail end of the compressor by connecting an exhaust channel 30 arranged on a main shaft and a flow guide channel 20 arranged on a flange. The main venting is achieved by means of a vent 10 in the flange.
Patent No. 201710916718.9 proposes a compressor structure, in which the main exhaust port is related to the same principle as patent No. 201510044276.4, and in order to ensure that the exhaust port area of the compressor is as large as possible, and reduce the exhaust loss, the sliding piece is required to completely cover the exhaust port when sweeping the exhaust port, so that when the exhaust port is increased, a rhombic exhaust port structure is required.
However, the above 2 patent solutions have two problems:
1. the exhaust channel formed by the exhaust channel 30 on the main shaft and the flow guide channel 20 on the flange is characterized in that the exhaust channel is opened as the pump body rotates due to the fact that no exhaust valve plate exists, when the exhaust channel 30 on the main shaft is communicated with the flow guide channel 20 on the flange, the exhaust channel is designed to be a constant pressure ratio, in order to meet all use requirements of existing air conditioners, the designed pressure ratio is larger than all working condition pressure ratios of operation of a compressor, otherwise, a partial working condition under-compression state (the exhaust pressure is not reached to start exhaust), the closer to the rear, the better the communication angle is, the exhaust channel only plays a role in auxiliary exhaust, and the utilization rate is not high.
2. When the displacement of the compressor is large, in order to increase the area of a large exhaust port and reduce exhaust loss, the number of the exhaust ports is increased besides the rhombic structure adopted by the exhaust port on the flange, so that the number of the exhaust valve sheet assemblies is increased, the number of parts of the compressor is increased, and the cost and the reliability hidden danger are improved; meanwhile, the flange is provided with an exhaust port structure, so that the rigidity of the flange is reduced, and the problems of abrasion and reliability can be caused; in addition, because the position of the exhaust port is fixed, after the cavity passes through the exhaust port of a certain flange (diamond), the exhaust port is closed after exhaust, and the area of the exhaust port changes suddenly, so that the exhaust speed of the compressor changes suddenly, and the compressor has great hidden trouble in reliability.
3. Repeated compression caused by re-expansion of the exhaust port clearance volume as the sliding vane sweeps across the flange exhaust port causes compressor energy efficiency to decrease.
4. When the sliding sheet sweeps across the flange exhaust port, the air flow of the exhaust port may affect the operation of the sliding sheet, so that the sliding sheet is inclined or unstable due to the change of stress, and the reliability of the compressor is affected.
5. When the compressor rotates for one circle, the exhaust valve plate is opened for N times (N is the number of sliding pieces), and the valve plate is easy to break in high-frequency operation, so that the reliability problem is solved.
Because the exhaust port of the compressor in the prior art is arranged on the flange and is opposite to the compression cavity, when the cavity is closed after exhausting after passing through the exhaust port of a certain flange, the area of the exhaust port is suddenly changed, so that the exhaust speed of the compressor is suddenly changed, and the problem of larger hidden trouble to the reliability of the compressor is solved.
Disclosure of Invention
Therefore, the technical problem to be solved by the invention is to overcome the defect that the sudden change of the exhaust speed of the compressor is caused by the sudden change of the area of the exhaust port of the compressor in the prior art, thereby providing the compressor and the air conditioner.
In order to solve the above problems, the present invention provides a compressor, comprising:
the main shaft comprises a convex part, the cylinder, the flange and the slip sheet jointly form a compression cavity, at least one main shaft exhaust port is formed in the convex part corresponding to each compression cavity, a flange exhaust port is formed in the flange, one end of each main shaft exhaust port is communicated with the compression cavity, the other end of each main shaft exhaust port can be communicated with the flange exhaust port in the main shaft rotating process to exhaust, an exhaust valve assembly is arranged in each main shaft exhaust port, and the exhaust valve assembly can automatically exhaust according to the pressure in the compression cavity;
the main shaft air outlet comprises a radial air outlet and an axial air outlet, the radial air outlet is formed in the radial outer side surface of the convex part and is formed in the radial direction, the axial air outlet is formed in the axial end surface of the convex part and is formed in the axial direction, and the axial air outlet is communicated with the radial air outlet so that air flow sequentially passes through the compression cavity, the radial air outlet and the axial air outlet;
the discharge valve subassembly includes ball valve and elastomeric element, the ball valve with elastomeric element set up in the radial gas vent, ball valve one end with elastomeric element links to each other, the other end with the radial gas vent sets up relatively, the ball valve can be reciprocating motion makes the radial gas vent with the axial gas vent switches between the intercommunication and the closed intercommunication.
Preferably, the exhaust valve assembly further comprises a blocking member provided in the radial exhaust port at a position between an outer end face of the radial exhaust port and the ball valve.
Preferably, the blocking component is a ring-shaped blocking ring structure, and the blocking component is radially installed in the radial exhaust port from the outer end face of the radial exhaust port; or the blocking component is of a baffle structure and is installed into the radial exhaust port from the axial exhaust port along the axial direction.
Preferably, the diameter of the radial exhaust port is defined as D, and when the blocking component is a ring-shaped baffle ring structure, the outer diameter of the baffle ring structure is D, the wall thickness is A, and A is more than or equal to 0.5mm, and/or D-D is more than or equal to 0.01mm and less than or equal to 0.2 mm.
Preferably, when the blocking member is a baffle structure, the position of the axial exhaust port on the convex part is further provided with a baffle installation groove for accommodating the baffle structure to be installed and inserted therein.
Preferably, the number of the radial exhaust ports is at least two, and the radial exhaust ports are arranged at intervals along the axial direction of the main shaft; and/or the axial exhaust port penetrates through the upper end surface and the lower end surface of the convex part along the axial direction of the main shaft.
Preferably, the convex part is further provided with at least one slide sheet groove, the slide sheet is arranged in the slide sheet groove, and the spindle air outlet is arranged at a position, close to the compression end, of the slide sheet groove along the circumferential direction.
Preferably, when the number of the slide sheet grooves is two or more, the spindle air outlet is arranged at a position between two adjacent slide sheet grooves along the circumferential direction, and the spindle air outlet is relatively close to the position of the slide sheet groove at the compression end.
Preferably, the flange gas vent includes flange gas vent groove and flange exhaust hole, the flange gas vent groove set up in the flange with on the axial one terminal surface that the convex part meets and set up along axial direction, the flange exhaust hole set up in the flange with on the other axial terminal surface that the convex part carried on the back mutually and set up along axial direction, the one end of flange gas vent groove with flange exhaust hole intercommunication, the other end of flange gas vent groove can the main shaft rotate the in-process with the main shaft gas vent intercommunication.
Preferably, the flange air discharge groove is an arc-shaped groove extending along the circumferential direction, the number of the flange air discharge holes is at least one, and at least one of the flange air discharge holes is communicated with the flange air discharge groove.
Preferably, the starting angle of the flange exhaust groove is β, the suction ending angle of the pump body cavity of the compressor is α, and the following conditions are satisfied: alpha is more than or equal to beta.
Preferably, the flange comprises an upper flange and a lower flange, the upper flange is provided with the flange exhaust port and/or the lower flange is provided with the flange exhaust port;
and/or, when the pressure in the compression cavity 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 cavity is less than the preset exhaust pressure, the exhaust valve assembly is closed to not exhaust;
and/or the compressor is a sliding vane compressor.
The invention also provides an air conditioner, which comprises the compressor.
The compressor and the air conditioner provided by the invention have the following beneficial effects:
the exhaust port is arranged on the convex part of the main shaft, the existing exhaust structure arranged on the flange at the position corresponding to the compression cavity is effectively eliminated, the convex part rotates along with the main shaft, so that the main shaft exhaust port is always positioned between the two sliding sheets, the exhaust valve component is arranged in the main shaft exhaust port and can automatically open the exhaust valve component to exhaust or close the exhaust according to the size in the compression cavity, when the pressure in the compression cavity is more than or equal to the preset exhaust pressure, the exhaust valve component is opened to exhaust, and when the pressure in the compression cavity is less than the preset exhaust pressure, the exhaust valve component is closed without exhausting; the structure design of the main shaft exhaust port, the exhaust valve assembly and the flange exhaust port is adopted, the quantity and the area of the exhaust ports in each compression cavity are effectively guaranteed to be fixed, the compressor can be guaranteed to normally run under all working conditions while the requirement of the exhaust speed of the compressor is met, and the exhaust speed is continuously changed;
2. in addition, because the exhaust is not needed to be carried out from the flange exhaust port opposite to the compression cavity, the problem of large power consumption caused by recompression due to the expansion of the clearance volume of the original flange exhaust port is effectively solved, and the energy efficiency of the compressor is improved; the air flow influence can be generated on the head of the sliding sheet when the original flange air outlet corresponding to the compression cavity exhausts air, and the air outlet of the main shaft is arranged on the convex part of the main shaft, so that the sliding sheet movement is not influenced by the air flow of the flange air outlet, and the reliability of the compressor is ensured; the utility model provides a rotatory a week of compressor, the ball valve is opened once, improves the ball valve reliability, effectively solves among the prior art every rotatory a week of compressor, and N times (N is gleitbretter quantity) are opened to the discharge valve piece, and the easy reliability problems such as fracture take place of valve piece high frequency operation.
Drawings
FIG. 1 is an exploded view of the pump body portion of the compressor of the present invention;
FIG. 2 is a cross-sectional view of the pump body during the suction/compression phase of the compressor of the present invention (with the ball valve not open);
FIG. 3 is a partial enlarged view in section of the location of the discharge port during the suction/compression phase of the present invention (partial enlarged view of portion R of FIG. 2);
FIG. 4 is a cross-sectional view of the pump body at the discharge stage of the compressor of the present invention (with the ball valve open);
FIG. 5 is a partial enlarged view in section of the exhaust port position in the exhaust stage of the present invention (partial enlarged view of portion Q of FIG. 4);
FIG. 6 is a schematic view of the pump body looking down on the flange vent slot and the end angle of suction;
FIG. 7 is an exploded structural view of the spindle assembly of the present invention;
FIG. 8 is a perspective view and a front view of the main shaft of the present invention;
FIG. 9 is a front and perspective view of the baffle ring of the present invention;
FIG. 10 is a perspective view of the lower end face and the upper end face, respectively, of the upper flange of the present invention;
FIG. 11 is a perspective view of the lower end face and the upper end face, respectively, of the lower flange of the present invention;
FIG. 12 is an exploded structural view of a spindle assembly of an alternative embodiment 1 of the present invention;
FIG. 13 is a front view structural diagram and a sectional view A-A of a main shaft of alternative embodiment 1 of the present invention;
FIG. 14 is an exploded structural view of a spindle assembly of an alternative embodiment 2 of the present invention;
FIG. 15 is a front view structural diagram and a sectional view B-B of a main shaft of alternative embodiment 2 of the present invention;
fig. 16 is a perspective view of a spindle according to alternative embodiment 2 of the present invention.
The reference numerals are represented as:
1. a main shaft; 11. a convex portion; 12. a slide groove; 100. a compression chamber; 2. a cylinder; 3. a flange; 31. an upper flange; 32. a lower flange; 4. sliding blades; 5. a main shaft exhaust port; 51. a radial exhaust port; 52. an axial exhaust port; 6. a flange exhaust port; 61. a flange vent slot; 62. a flange vent hole; 7. a vent valve assembly; 71. A ball valve; 72. an elastic member; 73. a blocking member; 74. a baffle plate mounting groove; 8. and (7) a cover plate.
Detailed Description
As shown in fig. 1 to 16, the present invention provides a compressor, which includes:
the compressor comprises a main shaft 1, a cylinder 2, a flange 3 and a sliding sheet 4, wherein the main shaft 1 comprises a convex part 11, the cylinder 2, the flange 3 and the sliding sheet 4 together form a compression cavity 100, at least one spindle exhaust port 5 is opened on the convex portion 11 corresponding to each compression chamber 100, the flange 3 is provided with flange exhaust ports 6 (preferably, the flange exhaust ports are arranged opposite to the main shaft exhaust ports in the radial direction, and can ensure the communication between the flange exhaust ports and the main shaft exhaust ports in the radial direction), one end of each main shaft exhaust port 5 is communicated with the compression cavity 100, the other end of each main shaft exhaust port can be communicated with the flange exhaust ports 6 in the rotation process of the main shaft so as to exhaust, an exhaust valve assembly 7 is arranged in the main shaft exhaust port 5, and the exhaust valve assembly 7 can automatically exhaust according to the pressure in the compression cavity 100;
the spindle exhaust port 5 comprises a radial exhaust port 51 and an axial exhaust port 52, the radial exhaust port 51 is arranged on the radial outer side surface of the convex part 11 and is arranged along the radial direction, the axial exhaust port 52 is arranged on the axial end surface of the convex part 11 and is arranged along the axial direction, and the axial exhaust port 52 is communicated with the radial exhaust port 51, so that air flow sequentially passes through the compression cavity 100, the radial exhaust port 51 and the axial exhaust port 52;
the exhaust valve assembly 7 includes a ball valve 71 and an elastic member 72 (preferably, a spring), the ball valve 71 and the elastic member 72 are disposed in the radial exhaust port 51, one end of the ball valve 71 is connected to the elastic member 72, and the other end is disposed opposite to the radial exhaust port 51, and the ball valve 71 can reciprocate to switch between communication and closed communication between the radial exhaust port 51 and the axial exhaust port 52.
According to the invention, the exhaust port is arranged on the convex part of the main shaft, the existing exhaust structure arranged on the flange at a position corresponding to the compression cavity is effectively eliminated, the convex part rotates along with the main shaft, so that the main shaft exhaust port is always positioned between the two sliding sheets, the exhaust valve component is arranged in the main shaft exhaust port, and the exhaust valve component can be automatically opened to exhaust or closed to exhaust according to the size in the compression cavity, when the pressure in the compression cavity 100 is more than or equal to the preset exhaust pressure, the exhaust valve component 7 is opened to exhaust, and when the pressure in the compression cavity 100 is less than the preset exhaust pressure, the exhaust valve component 7 is closed without exhausting; the structure design of the main shaft exhaust port, the exhaust valve assembly and the flange exhaust port is adopted, the quantity and the area of the exhaust ports in each compression cavity are effectively guaranteed to be fixed, the compressor can be guaranteed to normally run under all working conditions while the requirement of the exhaust speed of the compressor is met, and the exhaust speed is continuously changed;
the main shaft exhaust port comprises a radial exhaust port, and can be communicated with a compression cavity through the radial exhaust port and introduce gas, the axial exhaust port is used for communicating the gas from the radial exhaust port and introducing the gas into a flange exhaust port to effectively exhaust, the structure that the exhaust port is arranged on a flange opposite to the compression cavity in the prior art is effectively replaced and cancelled, the quantity and area of the exhaust port in each compression cavity are effectively ensured to be fixed, and the exhaust speed is continuously changed;
according to the invention, through the structures of the ball valve and the elastic component, the initial state of the ball valve can be abutted to the radial exhaust port by utilizing the elastic force of the elastic component to close exhaust when the pressure in the compression cavity is lower (as shown in figures 2-3), but when the pressure in the compression cavity is higher than the preset exhaust pressure, the pressure overcomes the sum of the elastic pressure and the high pressure of the exhaust end introduced into the axial exhaust port, the ball valve is pushed to move towards the direction far away from the radial exhaust port, the radial exhaust port is opened, the radial exhaust port is communicated with the axial exhaust port, so that the automatic exhaust is realized when the pressure is higher than the preset exhaust pressure value, and the automatic exhaust is closed when the pressure is lower than the preset exhaust pressure value (as shown in figures 4-5).
In addition, because the exhaust is not needed to be carried out from the flange exhaust port opposite to the compression cavity, the problem of large power consumption caused by recompression due to the expansion of the clearance volume of the original flange exhaust port is effectively solved, and the energy efficiency of the compressor is improved; the air flow influence can be generated on the head of the sliding sheet when the original flange air outlet corresponding to the compression cavity exhausts air, and the air outlet of the main shaft is arranged on the convex part of the main shaft, so that the sliding sheet movement is not influenced by the air flow of the flange air outlet, and the reliability of the compressor is ensured; the utility model provides a rotatory a week of compressor, the ball valve is opened once, improves the ball valve reliability, effectively solves among the prior art every rotatory a week of compressor, and N times (N is gleitbretter quantity) are opened to the discharge valve piece, and the easy reliability problems such as fracture take place of valve piece high frequency operation.
When the pressure of a compression cavity is higher than the comprehensive acting force of the external exhaust pressure of the pump body and the spring force of a valve spring, the ball valve moves along the radial exhaust hole, the cavity is communicated with the flange exhaust groove through the main shaft exhaust hole and is exhausted out of the pump body of the compressor through the flange exhaust hole, and the exhaust of the compressor is realized. The quantity and the area of the exhaust ports in each compression cavity are fixed, the requirement of the exhaust speed of the compressor is met, the compressor is guaranteed to normally operate under all working conditions, the exhaust speed is continuously changed, the problem of large power consumption caused by recompression due to the expansion of the clearance volume of the exhaust ports of the original flange is solved, and the energy efficiency of the compressor is improved. Meanwhile, the sliding vane movement is not influenced by the air flow of the flange exhaust port, and the reliability of the compressor is ensured.
Preferably, the exhaust valve assembly 7 further includes a blocking member 73, and the blocking member 73 is disposed in the radial exhaust port 51 at a position between an outer end surface of the radial exhaust port 51 and the ball valve 71. The exhaust valve assembly is further preferred in structural form, and the structural form of the blocking component can limit one end of the ball valve, which is far away from the elastic component, so that the ball valve is prevented from being separated from the outer end face of the radial exhaust port.
With reference to fig. 2 and 3, since the pressure of the cavity does not reach the discharge pressure during the suction or compression process of the compressor, the ball valve presses the retainer ring under the action of the acting force of the spring (given initial pretightening force) and the exhaust back pressure of the housing, so as to realize the isolation of the radial exhaust port and the axial exhaust port of the main shaft, i.e., the compression cavity is isolated from the outside of the pump body, thereby ensuring the sealing.
With reference to fig. 4, 5 and 6, when the pressure of the compression cavity is higher than the combined action force of the external exhaust pressure of the pump body and the spring force of the spring, the ball valve moves along the radial exhaust port direction, the main shaft radial exhaust port is communicated with the axial exhaust port and the flange exhaust groove, and the main shaft radial exhaust port is exhausted out of the compressor pump body through the flange exhaust hole, so that the compressor is exhausted.
Preferably, the blocking member 73 is a ring-shaped baffle ring structure, and the blocking member 73 is radially inserted into the radial exhaust port 51 from the outer end surface of the radial exhaust port 51; or the blocking member 73 is a baffle structure, and the blocking member 73 is axially inserted into the radial exhaust port 51 from the axial exhaust port 52. This is a further preferred structural form of the blocking member of the present invention, and in the main embodiment, as shown in fig. 9 and 11, the blocking member is a circular ring structure and is radially installed in the radial exhaust port, which can allow the airflow to pass through and be exhausted from the radial exhaust port and the ball valve toward the axial exhaust port, the spring, the ball valve and the baffle ring are sequentially installed in the radial exhaust port of the main shaft, and the baffle ring and the radial exhaust port of the main shaft adopt interference fit, so that a certain interference is required to ensure reliable installation; in an alternative embodiment, as shown in fig. 14-16, the blocking member is a baffle structure and is axially installed in the radial exhaust port, so as to effectively perform the blocking and thrust functions.
Preferably, the diameter of the radial exhaust port 51 is defined as D, and when the blocking component 73 is a ring-shaped baffle ring structure, the outer diameter of the baffle ring structure is D, the wall thickness is A, and A is greater than or equal to 0.5mm, and/or 0.01mm is greater than or equal to D-D is less than or equal to 0.2 mm. A is more than or equal to 0.5mm, the strength of the baffle ring can be effectively ensured, D-D is more than or equal to 0.01mm and less than or equal to 0.2mm, the baffle ring can be ensured to be arranged into the radial exhaust port in an interference manner along the radial direction, meanwhile, the main shaft is ensured not to generate large deformation during installation, and the interference magnitude has certain requirements.
Preferably, when the blocking member 73 is a baffle structure, the position of the axial exhaust port 52 on the convex portion 11 is further provided with a baffle installation groove 74 to accommodate the baffle structure to be installed and inserted therein. The second preferred structural form of the second alternative embodiment of the invention is that the baffle installation groove is started at the axial exhaust port, so that the baffle can be effectively installed, and meanwhile, an effective clamping effect is formed, and the ball valve is effectively limited.
Preferably, the number of the radial exhaust ports 51 is at least two, and the radial exhaust ports are arranged at intervals along the axial direction of the main shaft; and/or the axial exhaust port 52 penetrates the upper and lower end surfaces of the convex portion 11 in the axial direction of the main shaft. This is a preferred configuration form of the first alternative embodiment of the present invention, as shown in fig. 12-13, the number of the radial exhaust ports is multiple, and 3 radial exhaust ports are shown in the figure and arranged side by side along the axial direction, so that the exhaust can be performed simultaneously through the multiple radial exhaust ports, the exhaust area is increased, the exhaust speed is increased, and the axial exhaust ports penetrate through the upper and lower end faces of the convex portion to ensure that each radial exhaust port can be communicated with the flange exhaust groove and the exhaust port, thereby enhancing the exhaust effect.
Preferably, the protrusion 11 further has at least one sliding vane groove 12, the sliding vane 4 is disposed in the sliding vane groove 12, and the spindle air outlet 5 is disposed at a position (relative to the compression air suction end) of the sliding vane groove 12 along the circumferential direction, which is relatively close to the compression end. Further preferably, when the number of the slide sheet grooves 12 is two or more, the spindle air outlet 5 is disposed at a position between two adjacent slide sheet grooves 12 in the circumferential direction, and the spindle air outlet 5 is relatively close to the slide sheet groove 12 at the compression end. The preferable structural relationship between the slide sheet groove and the main shaft air outlet is that a main shaft air outlet is arranged between the two slide sheet grooves in the circumferential direction, and certainly, more than two or more main shaft air outlets can be arranged between the two slide sheet grooves, and the main shaft air outlet is arranged close to the slide sheet groove at the compression end, so that the clearance volume existing between the main shaft air outlet and the slide sheet in the compression cavity can be effectively reduced, and the compression efficiency is improved, as shown in fig. 6.
As shown in fig. 10 to 11, preferably, the flange exhaust port 6 includes a flange exhaust groove 61 and a flange exhaust hole 62, the flange exhaust groove 61 is disposed on one axial end surface of the flange 3 that is connected to the convex portion 11 and is opened along an axial direction, the flange exhaust hole 62 is disposed on the other axial end surface of the flange 3 that is opposite to the convex portion 11 and is opened along the axial direction, one end of the flange exhaust groove 61 is communicated with the flange exhaust hole 62, and the other end of the flange exhaust groove 61 can be communicated with the spindle exhaust port 5 during the rotation of the spindle 1. The flange exhaust port is preferably in a structural form, namely, the flange exhaust grooves arranged on the axial end face connected with the convex part can be respectively communicated with one or more main shaft exhaust grooves and can be exhausted through the flange exhaust holes on the other end face, the communication effect with the main shaft exhaust port can be ensured to the maximum extent through the structure of the flange exhaust grooves, the main shaft exhaust port is prevented from being incapable of communicating with exhaust gas when the exhaust gas is needed, and the flange exhaust holes arranged on the other end face at intervals can increase the structural strength and rigidity of the flange and meet the exhaust requirement at the same time.
Preferably, the flange air discharge groove 61 is an arc-shaped groove extending along the circumferential direction, the number of the flange air discharge holes 62 is at least one, and at least one of the flange air discharge holes 62 is communicated with the flange air discharge groove 61. The flange exhaust groove and the flange exhaust hole are further preferred in structural form, the circumferentially extending arc-shaped groove structure can further guarantee the communication effect with a plurality of main shaft exhaust holes, effective exhaust requirements are guaranteed, and at least one flange exhaust hole can be communicated with the flange exhaust groove to meet exhaust requirements and improve the structural strength and rigidity of the flange (without arranging a through groove).
As shown in fig. 6, preferably, the starting angle of the flange discharge groove 61 is β, the pump body cavity suction ending angle of the compressor is α, and the following conditions are satisfied: alpha is more than or equal to beta. Through the structure, the main shaft air outlet in the compression cavity of the compression section can be effectively communicated to the flange air outlet groove, the situation that the position of the main shaft air outlet in the partial compression cavity cannot be communicated to the flange air outlet groove is prevented, all working condition situations cannot be met, and the effect that all working conditions (different pressure ratios) can be achieved is achieved.
FIG. 6 is a schematic diagram illustrating the relationship between the flange exhaust groove and the suction end angle in a top view. In order to meet the use requirements of all working conditions (different pressure ratios, particularly when the pressure ratio is 1), the initial angle beta of the flange exhaust groove and the suction end angle alpha of the cavity of the pump body of the compressor meet the following requirements: alpha is more than or equal to beta. Meanwhile, in order to ensure other complete discharge, the separation angle of the flange exhaust groove and the main shaft exhaust port is positioned behind the tangent position of the main shaft and the inner diameter of the cylinder.
Preferably, the flange 3 comprises an upper flange 31 and a lower flange 32, the upper flange 31 is provided with the flange exhaust port 6, and/or the lower flange 32 is provided with the flange exhaust port 6;
and/or, when the pressure in the compression cavity 100 is greater than or equal to a preset exhaust pressure, the exhaust valve assembly 7 is opened to perform exhaust, and when the pressure in the compression cavity 100 is less than the preset exhaust pressure, the exhaust valve assembly 7 is closed to perform no exhaust;
and/or the compressor is a sliding vane compressor.
The flange is an optimal structure form of the flange, the exhaust area can be increased and the exhaust effect can be improved by arranging the flange exhaust ports on the upper flange and the lower flange, the flange exhaust grooves and the flange exhaust holes (corresponding to the radial exhaust ports and the axial ports of the main shaft) can be arranged on the upper flange or the lower flange only according to requirements, and when the exhaust area is limited by the structure and is insufficient, the flange exhaust grooves and the flange exhaust holes can be arranged on the upper flange and the lower flange at the same time. With reference to fig. 12 and 13, the flange vent holes are disposed in the flange vent grooves, and the number of the flange vent holes is not limited, so as to communicate the flange vent grooves with the outside of the pump body. When the compressor exhausts, airflow firstly passes through the main shaft exhaust port, opens the exhaust ball valve, enters the flange exhaust groove, and is exhausted out of the pump body through the flange exhaust hole.
According to the invention, when the pressure in the compression cavity 100 is greater than or equal to the preset exhaust pressure (the preset exhaust pressure is the preset elastic force of the elastic component plus the exhaust pressure of the exhaust cavity), the exhaust valve assembly 7 is opened to exhaust, and when the pressure in the compression cavity 100 is smaller than the preset exhaust pressure, the exhaust valve assembly 7 is closed to avoid exhausting, so that automatic exhaust can be realized through the exhaust valve assembly according to the pressure in the compression cavity.
The invention also provides an air conditioner, which comprises the compressor. The exhaust mode of the invention adopts the structural design of a main shaft exhaust port, an exhaust valve, a flange exhaust groove and a flange exhaust hole, the main shaft is provided with an exhaust port, the exhaust valve is installed, the flange is provided with the flange exhaust groove and the flange exhaust hole, when the pressure of a compression cavity is higher than the comprehensive acting force of the external exhaust pressure of a pump body and the spring force of a spring, a ball valve moves along the direction of the radial exhaust port, the radial exhaust port of the main shaft is communicated with the axial exhaust port and is communicated with the flange exhaust groove, and the pump body of the compressor is exhausted through the flange exhaust hole, so that the exhaust of the compressor is realized. The quantity and the area of the exhaust ports in each compression cavity are fixed, the requirement of the exhaust speed of the compressor is met, the compressor is guaranteed to normally operate under all working conditions, the exhaust speed is continuously changed, the problem of large power consumption caused by recompression due to the expansion of the clearance volume of the exhaust ports of the original flange is solved, and the energy efficiency of the compressor is improved. Meanwhile, the sliding vane movement is not influenced by the air flow of the flange exhaust port, and the reliability of the compressor is ensured.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents and improvements made within the spirit and principle of the present invention are intended to be included within the scope of the present invention. The above description is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, several modifications and variations can be made without departing from the technical principle of the present invention, and these modifications and variations should also be regarded as the protection scope of the present invention.
Claims (10)
1. A compressor, characterized by: the method comprises the following steps:
a main shaft (1), a cylinder (2), a flange (3) and a slip sheet (4), the main shaft (1) comprises a convex part (11), the cylinder (2), the flange (3) and the sliding sheet (4) jointly form a compression cavity (100), at least one main shaft exhaust port (5) is arranged on the convex part (11) corresponding to each compression cavity (100), the flange (3) is provided with flange exhaust ports (6), one end of each main shaft exhaust port (5) is communicated with the compression cavity (100), the other end of each main shaft exhaust port can be communicated with the flange exhaust port (6) in the rotating process of the main shaft to exhaust, and an exhaust valve assembly (7) is arranged in the main shaft exhaust port (5), the exhaust valve assembly (7) can automatically exhaust according to the pressure in the compression cavity (100);
the spindle exhaust port (5) comprises a radial exhaust port (51) and an axial exhaust port (52), the radial exhaust port (51) is arranged on the radial outer side surface of the convex part (11) and is arranged along the radial direction, the axial exhaust port (52) is arranged on the axial end surface of the convex part (11) and is arranged along the axial direction, and the axial exhaust port (52) is communicated with the radial exhaust port (51), so that airflow sequentially passes through the compression cavity (100), the radial exhaust port (51) and the axial exhaust port (52);
the exhaust valve assembly (7) comprises a ball valve (71) and an elastic component (72), the ball valve (71) and the elastic component (72) are arranged in the radial exhaust port (51), one end of the ball valve (71) is connected with the elastic component (72), the other end of the ball valve is arranged opposite to the radial exhaust port (51), and the ball valve (71) can reciprocate to enable the radial exhaust port (51) and the axial exhaust port (52) to be switched between communication and closed communication;
when the pressure in the compression cavity is higher than the preset exhaust pressure, the pressure overcomes the sum of the elastic force and the high pressure of an exhaust end introduced into the axial exhaust port, the ball valve is pushed to move in the direction away from the radial exhaust port, the radial exhaust port is opened, the radial exhaust port is communicated with the axial exhaust port, so that the radial exhaust port automatically exhausts when the pressure is higher than the preset exhaust pressure value, and the automatic exhaust is closed when the pressure is lower than the preset exhaust pressure value;
the flange exhaust port (6) comprises a flange exhaust groove (61) and a flange exhaust hole (62), the flange exhaust groove (61) is arranged on one axial end face of the flange (3) connected with the convex part (11) and is formed in the axial direction, the flange exhaust hole (62) is arranged on the other axial end face of the flange (3) opposite to the convex part (11) and is formed in the axial direction, one end of the flange exhaust groove (61) is communicated with the flange exhaust hole (62), and the other end of the flange exhaust groove (61) can be communicated with the spindle exhaust port (5) in the rotation process of the spindle (1);
the flange exhaust groove (61) is an arc-shaped groove extending along the circumferential direction, the number of the flange exhaust holes (62) is at least one, and at least one flange exhaust hole (62) is communicated with the flange exhaust groove (61);
the initial angle of the flange exhaust groove (61) is beta, the suction end angle of a pump body cavity of the compressor is alpha, and the suction end angle satisfies the following conditions: alpha is more than or equal to beta; the separation angle of the flange exhaust groove (61) and the main shaft exhaust port is positioned behind the tangent position of the main shaft and the inner diameter of the cylinder.
2. The compressor of claim 1, wherein:
the exhaust valve assembly (7) further includes a blocking member (73), the blocking member (73) being provided in the radial exhaust port (51) at a position between an outer end surface of the radial exhaust port (51) and the ball valve (71).
3. The compressor of claim 2, wherein:
the blocking component (73) is of an annular blocking ring structure, and the blocking component (73) is installed in the radial exhaust port (51) from the outer end face of the radial exhaust port (51) in the radial direction; or the blocking component (73) is of a baffle structure, and the blocking component (73) is axially installed into the radial exhaust port (51) from the axial exhaust port (52).
4. A compressor according to claim 3, wherein:
the diameter of the radial exhaust port (51) is defined as D, and when the blocking component (73) is a circular ring-shaped blocking ring structure, the outer diameter of the blocking ring structure is D, the wall thickness of the blocking ring structure is A, and A is more than or equal to 0.5mm, and/or D-D is more than or equal to 0.01mm and less than or equal to 0.2 mm.
5. A compressor according to claim 3, wherein:
when the blocking component (73) is of a baffle structure, a baffle mounting groove (74) is further formed in the position of the axial exhaust port (52) on the convex portion (11) to accommodate the baffle structure to be mounted and inserted into.
6. The compressor according to any one of claims 1 to 5, wherein:
the number of the radial exhaust ports (51) is at least two, and the radial exhaust ports are arranged at intervals along the axial direction of the main shaft; and/or the axial exhaust port (52) penetrates through the upper end surface and the lower end surface of the convex part (11) along the axial direction of the main shaft.
7. The compressor according to any one of claims 1 to 5, wherein:
the convex part (11) is further provided with at least one sliding sheet groove (12), the sliding sheet (4) is arranged in the sliding sheet groove (12), and the spindle exhaust port (5) is arranged at the position, close to the compression end, of the sliding sheet groove (12) along the circumferential direction.
8. The compressor of claim 7, wherein:
when the number of the slide sheet grooves (12) is more than two, the main shaft air outlet (5) is arranged at a position between two adjacent slide sheet grooves (12) along the circumferential direction, and the main shaft air outlet (5) is relatively close to the position of the slide sheet groove (12) at the compression finishing end.
9. The compressor according to any one of claims 1 to 5, wherein:
the flange (3) comprises an upper flange (31) and a lower flange (32), the upper flange (31) is provided with the flange exhaust port (6) and/or the lower flange (32) is provided with the flange exhaust port (6);
and/or, 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 to not exhaust;
and/or the compressor is a sliding vane compressor.
10. An air conditioner, characterized in that: comprising a compressor according to any one of claims 1-9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010728223.5A CN111963435B (en) | 2020-07-24 | 2020-07-24 | Compressor and air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010728223.5A CN111963435B (en) | 2020-07-24 | 2020-07-24 | Compressor and air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN111963435A CN111963435A (en) | 2020-11-20 |
| CN111963435B true CN111963435B (en) | 2022-08-05 |
Family
ID=73362865
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010728223.5A Active CN111963435B (en) | 2020-07-24 | 2020-07-24 | Compressor and air conditioner |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN111963435B (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117145766A (en) * | 2022-05-23 | 2023-12-01 | 珠海格力电器股份有限公司 | Fluid machine and heat exchange device |
| CN117145773A (en) * | 2022-05-23 | 2023-12-01 | 珠海格力电器股份有限公司 | Fluid machine and heat exchange device |
| CN117145768A (en) * | 2022-05-23 | 2023-12-01 | 珠海格力电器股份有限公司 | Fluid machine and heat exchange device |
| CN117145771A (en) * | 2022-05-23 | 2023-12-01 | 珠海格力电器股份有限公司 | Fluid machine and heat exchange device |
Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60206996A (en) * | 1984-03-31 | 1985-10-18 | Shimadzu Corp | Vacuum pump |
| JPS6425486U (en) * | 1987-08-05 | 1989-02-13 | ||
| CN202132202U (en) * | 2011-05-13 | 2012-02-01 | 珠海格力电器股份有限公司 | Two-stage compressor and upper flange component thereof |
| CN103672053A (en) * | 2012-09-18 | 2014-03-26 | 日立汽车系统株式会社 | Pump apparatus |
| CN103939355A (en) * | 2014-04-25 | 2014-07-23 | 珠海凌达压缩机有限公司 | Compressor exhaust device and compressor provided with same |
| CN204083386U (en) * | 2014-08-21 | 2015-01-07 | 张树利 | A kind of check valve |
| CN104302923A (en) * | 2012-05-18 | 2015-01-21 | 卡森尼可关精株式会社 | Gas compressor |
| CN106762660A (en) * | 2017-02-27 | 2017-05-31 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of compressor main shaft and the compressor with it |
| CN107061268A (en) * | 2017-03-31 | 2017-08-18 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of screw compressor and its refrigerant supplementing structure |
| CN107542658A (en) * | 2017-09-29 | 2018-01-05 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and there is its air conditioner |
| CN105987004B (en) * | 2015-01-28 | 2018-02-06 | 珠海格力节能环保制冷技术研究中心有限公司 | Sliding-vane compressor and its exhaust structure |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN208686581U (en) * | 2018-08-21 | 2019-04-02 | 珠海格力电器股份有限公司 | The pump housing and compressor with it |
-
2020
- 2020-07-24 CN CN202010728223.5A patent/CN111963435B/en active Active
Patent Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60206996A (en) * | 1984-03-31 | 1985-10-18 | Shimadzu Corp | Vacuum pump |
| JPS6425486U (en) * | 1987-08-05 | 1989-02-13 | ||
| CN202132202U (en) * | 2011-05-13 | 2012-02-01 | 珠海格力电器股份有限公司 | Two-stage compressor and upper flange component thereof |
| CN104302923A (en) * | 2012-05-18 | 2015-01-21 | 卡森尼可关精株式会社 | Gas compressor |
| CN103672053A (en) * | 2012-09-18 | 2014-03-26 | 日立汽车系统株式会社 | Pump apparatus |
| CN103939355A (en) * | 2014-04-25 | 2014-07-23 | 珠海凌达压缩机有限公司 | Compressor exhaust device and compressor provided with same |
| CN204083386U (en) * | 2014-08-21 | 2015-01-07 | 张树利 | A kind of check valve |
| CN105987004B (en) * | 2015-01-28 | 2018-02-06 | 珠海格力节能环保制冷技术研究中心有限公司 | Sliding-vane compressor and its exhaust structure |
| CN106762660A (en) * | 2017-02-27 | 2017-05-31 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of compressor main shaft and the compressor with it |
| CN107061268A (en) * | 2017-03-31 | 2017-08-18 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of screw compressor and its refrigerant supplementing structure |
| CN107542658A (en) * | 2017-09-29 | 2018-01-05 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and there is its air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| CN111963435A (en) | 2020-11-20 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN111963435B (en) | Compressor and air conditioner | |
| WO2022016934A1 (en) | Compressor and air conditioner | |
| US4611977A (en) | Vane compressor with vane back pressure adjustment | |
| CN111963431A (en) | Compressor and air conditioner | |
| CN111963429B (en) | Pump body subassembly, compressor and air conditioner | |
| CN111963432B (en) | Compressor and air conditioner | |
| JPH0581759B2 (en) | ||
| EP1690007B1 (en) | Two stage scroll vacuum pump | |
| CN111963433B (en) | Compressor and air conditioner | |
| CN212202465U (en) | Compression mechanism and scroll compressor | |
| CN100424355C (en) | Discharge valve device of rotary compressor | |
| CN111963430B (en) | Pump body subassembly, compressor and air conditioner | |
| JP5843729B2 (en) | Gas compressor | |
| CN111963434B (en) | Pump body subassembly, compressor and air conditioner | |
| CN114109836B (en) | Pump body structure of compressor and compressor | |
| JP4370037B2 (en) | Gas compressor | |
| EP3770435B1 (en) | Compressor pump body, compressor, and air conditioner | |
| CN112343818B (en) | Pump body structure and air conditioner | |
| CN111963428B (en) | Pump body subassembly, compressor and air conditioner | |
| WO2021220449A1 (en) | Rotary compressor | |
| KR100423125B1 (en) | Double compressor having planetary rotors | |
| KR100575838B1 (en) | Bypass valve assembly for capacity variable type rotary compressor | |
| CN100394033C (en) | By-pass valve assembly of rotary and capacity-variable compressor | |
| KR20010076889A (en) | Low pressure type rotary compressor | |
| CN117642556A (en) | Non-orbiting scroll assembly and scroll compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |