CN109026699B - Pump body, compressor and manufacturing method of pump body - Google Patents
Pump body, compressor and manufacturing method of pump body Download PDFInfo
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- CN109026699B CN109026699B CN201810953919.0A CN201810953919A CN109026699B CN 109026699 B CN109026699 B CN 109026699B CN 201810953919 A CN201810953919 A CN 201810953919A CN 109026699 B CN109026699 B CN 109026699B
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- 238000004519 manufacturing process Methods 0.000 title claims abstract description 12
- 238000003825 pressing Methods 0.000 claims abstract description 14
- 238000000034 method Methods 0.000 claims description 6
- 238000012545 processing Methods 0.000 claims description 6
- 238000013461 design Methods 0.000 abstract description 11
- 230000006835 compression Effects 0.000 abstract description 5
- 238000007906 compression Methods 0.000 abstract description 5
- 238000005096 rolling process Methods 0.000 description 7
- 241001391944 Commicarpus scandens Species 0.000 description 3
- 230000002159 abnormal effect Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
Classifications
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- 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
- F04C18/356—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 outer member
- F04C18/3562—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 outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
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- 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
- F04C2240/00—Components
- F04C2240/10—Stators
-
- 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
- F04C2240/20—Rotors
-
- 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
- F04C2240/80—Other components
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Abstract
The invention provides a pump body, a compressor and a manufacturing method of the pump body, which solve the technical problem that the service life of the compressor is seriously affected by easy breakage or relaxation of a pump body spring of the compressor, and adopts the technical scheme that: in the pump body, the groove depth H of the tail groove section of the sliding vane groove suitable for accommodating the spring is made to meet the following conditions: h is more than or equal to 1.5+Lmax; the free length L0 of the spring satisfies: l0 is more than or equal to 2+Lmax; the pressing height Lb of the spring meets the following conditions: lb is less than or equal to Lmin-2; wherein Lmin is the minimum working length of the spring and Lmax is the maximum working length of the spring. According to the invention, the reasonable design is carried out aiming at the relevant dimensions such as the depth of the spring hole of the air cylinder, the size of the spring and the like, so that when the sliding vane runs to the position where the sliding vane stretches out the longest, the compression amount of the spring can not cause the breakage of the spring because of overlarge, and when the sliding vane runs to the position where the sliding vane stretches out the longest, the head of the spring can always contact with the sliding vane, so that the spring can not relax and is always in a working state, and the following performance of the sliding vane and the eccentric rotating assembly is greatly improved.
Description
Technical Field
The invention relates to the technical field of rotary compressor pump body design, in particular to a pump body, a compressor and a manufacturing method of the pump body.
Background
The rotary compressor pump body structure comprises an upper flange, a cylinder, an eccentric crankshaft, a rolling rotor, a sliding vane, a lower flange and a spring, wherein a sliding vane groove is formed in the cylinder body of the cylinder, and the spring and the sliding vane are positioned in the sliding vane groove. When the compressor works, the pump body crankshaft drives the rolling rotor to rotate. The sliding vane reciprocates in the sliding vane groove, and the sliding vane makes its head contact closely with the outer circle of the rolling rotor to separate the working cavity enclosed by the cylinder and the upper and lower flanges into two parts, including low pressure cavity and high pressure cavity.
The spring is an important part of the pump body of the rolling rotor type compressor, especially for the variable frequency compressor, the rotating speed changes in a large range, the stress condition of the spring is very bad, the design quality of the spring can directly influence the reliability of the compressor, for example, the following property of a sliding vane, the existence of abnormal sound, leakage and the like during the working of the compressor are all related to the design quality of the spring.
In the prior art, the spring is designed mainly according to the gas force acted by the sliding vane, and the design of the spring meets the following requirements: the sliding vane is ensured to be always contacted with the rolling rotor in the running process. However, there is no proper standard for the design of the spring hole and the selection of the spring, so that the spring can ensure that the sliding sheet is always in contact with the rolling rotor in the running process, and the spring cannot be loosened or broken along with the high-strength working of the pump body. In the actual use process, the pump body is often broken because the spring does not bear the high-strength work of the pump body or can not always generate biasing force to the sliding sheets to relax, and the accidentally causes serious influence on the pump body of the compressor and even influences the service life of the compressor.
Therefore, how to solve the technical problem that the service life of the compressor is seriously affected due to the fact that the pump body spring of the compressor is easily broken or loosened is a great problem to be solved urgently by those skilled in the art.
Disclosure of Invention
Therefore, the invention aims to solve the technical problem that the service life of the compressor is seriously affected due to the fact that the pump body spring of the compressor is easy to break or loose, and provides the pump body, the compressor and the manufacturing method of the pump body.
In order to achieve the above object, the present invention adopts the technical scheme that:
a compressor pump body, comprising: the cylinder is provided with an inner cavity, a sliding vane groove is formed in the side wall of the inner cavity, and comprises a head groove section and a tail groove section communicated with the head groove section; the eccentric rotating assembly is arranged in the inner cavity; a spring positioned in the tail groove section; the sliding vane is arranged in the head groove section, the tail part of the sliding vane extends into the tail groove section, and when the eccentric rotating assembly rotates compressed gas along the side wall of the inner cavity, the spring continuously provides biasing force for the sliding vane to keep the head end of the sliding vane in contact with the eccentric rotating assembly; the groove depth H of the tail groove section meets the following conditions: h is more than or equal to 1.5+Lmax; the free length L0 of the spring satisfies: l0 is more than or equal to 2+Lmax; the pressing height Lb of the spring meets the following conditions: lb is less than or equal to Lmin-2; wherein Lmin is the minimum working length of the spring and Lmax is the maximum working length of the spring.
The sliding vane groove is a through groove, and the tail of the spring is flush with the tail end of the sliding vane groove.
The tail end of the sliding sheet is provided with a containing groove (31) for containing the head end of the spring.
Lmin= (D1-D2)/2- (T1-T2); lmax= (D2-D) + (D1-D2)/2- (T1-T2); wherein D1 is the outer diameter of the cylinder, D2 is the inner diameter of the cylinder, D is the outer diameter of the eccentric rotating assembly, T1 is the length of the sliding sheet along the extending or retracting direction, and T2 is the groove depth of the accommodating groove.
The eccentric rotation assembly comprises: the crankshaft penetrates through the inner cavity of the cylinder; the roller is sleeved on the crankshaft; the outer diameter d of the eccentric rotating assembly refers to the outer diameter of the roller.
The outer diameter of the cylinder refers to the outer diameter of the cylinder where the sliding vane groove is located.
The tail end of the sliding vane groove is provided with a bolt which is in threaded connection with an internal thread arranged on the inner wall of the tail end of the sliding vane groove.
A compressor comprising a pump body according to the above.
The manufacturing method of the compressor pump body comprises the following steps: acquiring a minimum working length Lmin value of the spring and a maximum working length Lmax value of the spring; according to the following relation: the groove depth H of the tail groove section meets the following conditions: h is more than or equal to 1.5+Lmax; the free length L0 of the spring satisfies: l0 is more than or equal to 2+Lmax; the pressing height Lb of the spring meets the following conditions: lb is less than or equal to Lmin-2; determining a groove depth H value of the tail groove section, wherein the free length L0 value of the spring and the pressing height of the spring are Lb values; and selecting a spring according to the L0 value and the Lb value, and processing the tail groove section according to the H value.
The sliding vane groove is a through groove, the tail end of the sliding vane is provided with a containing groove for containing the head end of the spring, and the following relation is adopted: lmin= (D1-D2)/2- (T1-T2); lmax= (D2-D) + (D1-D2)/2- (T1-T2); obtaining an Lmin value and an Lmax value; wherein D1 is the outer diameter of the cylinder, D2 is the inner diameter of the cylinder, D is the outer diameter of the eccentric rotating assembly, T1 is the length of the sliding sheet along the extending or retracting direction, and T2 is the groove depth of the accommodating groove.
The tail of the spring is flush with the tail end of the sliding vane groove, and the tail end of the sliding vane groove forms a positioning reference for measuring the groove depth H value of the tail groove section.
The technical scheme of the invention has the following advantages:
1. the present invention provides a compressor pump body, comprising: the cylinder is provided with an inner cavity, a sliding vane groove is formed in the side wall of the inner cavity, and comprises a head groove section and a tail groove section communicated with the head groove section; the eccentric rotating assembly is arranged in the inner cavity; a spring positioned in the tail groove section; the sliding vane is arranged in the head groove section, the tail part of the sliding vane extends into the tail groove section, and when the eccentric rotating assembly rotates compressed gas along the side wall of the inner cavity, the spring continuously provides biasing force for the sliding vane to keep the head end of the sliding vane in contact with the eccentric rotating assembly; the groove depth H of the tail groove section meets the following conditions: h is more than or equal to 1.5+Lmax; the free length L0 of the spring satisfies: l0 is more than or equal to 2+Lmax; the pressing height Lb of the spring meets the following conditions: lb is less than or equal to Lmin-2; wherein Lmin is the minimum working length of the spring and Lmax is the maximum working length of the spring.
The core technical scheme of the invention is that the springs and the processed tail groove sections are selected in the ranges of the three groups of formulas, so that when the sliding vane runs to the position where the sliding vane stretches out the shortest, the spring compression amount cannot cause the breakage of the springs due to overlarge spring, and when the sliding vane runs to the position where the sliding vane stretches out the longest, the head of the spring can always contact with the sliding vane, so that the springs cannot relax and are always in a working state, and the following performance of the sliding vane and the eccentric rotating assembly is greatly improved.
The spring is an important part of the compressor pump body, and the design requirement of the spring is that the service life of the spring directly determines the service life of the compressor pump body except for meeting the requirement of ensuring that a sliding vane is always contacted with a rolling rotor in the running process. However, in the prior art, the spring design can meet the following performance requirement during initial operation, but with the high-strength operation of the compressor pump body, gas leakage often occurs due to easy breakage or relaxation of the spring, even normal operation cannot be realized, and the service life of the compressor is influenced. Therefore, how to ensure that the spring can still continuously and efficiently work for a long time under severe stress, namely, the spring is not easy to break when working under high stress and is not easy to relax when working under high strength, and new requirements are put forward on the design of the spring. The invention designs a novel compressor pump body aiming at the requirements, so that the relative sizes of the spring and the compressor pump body component meet certain design requirements, and the spring is not easy to break when working under high stress and is not easy to relax when working under high strength, thereby greatly prolonging the service life of the spring and further prolonging the service life of the compressor pump body.
2. The tail end of the sliding vane is provided with the accommodating groove (31) for accommodating the head end of the spring, and Lmin= (D1-D2)/2- (T1-T2); lmax= (D2-D) + (D1-D2)/2- (T1-T2); wherein D1 is the outer diameter of the cylinder, D2 is the inner diameter of the cylinder, D is the outer diameter of the eccentric rotating assembly, T1 is the length of the sliding sheet along the extending or retracting direction, and T2 is the groove depth of the accommodating groove. The Lmin value and the Lmax value calculated according to the formula can also be obtained through a measuring means, and the invention preferably adopts D1, D2, D, T1 and T2 with known determined values to rapidly and accurately determine the Lmin and the Lmax, thereby reducing measuring errors and improving numerical accuracy.
3. The compressor provided by the invention comprises the pump body. All the advantages of the pump body described above are possessed.
4. The invention provides a manufacturing method of a compressor pump body, which comprises the following steps: acquiring a minimum working length Lmin value of the spring and a maximum working length Lmax value of the spring; according to the following relation: the groove depth H of the tail groove section meets the following conditions: h is more than or equal to 1.5+Lmax; the free length L0 of the spring satisfies: l0 is more than or equal to 2+Lmax; the pressing height Lb of the spring meets the following conditions: lb is less than or equal to Lmin-2; determining a groove depth H value of the tail groove section, wherein the free length L0 value of the spring and the pressing height of the spring are Lb values; and selecting a spring according to the L0 value and the Lb value, and processing the tail groove section according to the H value. Selecting springs with Lb and L0 values meeting requirements according to the formula Lb being less than or equal to Lmin-2 and L0 being less than or equal to 2+Lmax, and processing the tail groove section H according to the formula H being less than or equal to 1.5+Lmax. The spring and the processed tail groove section selected in the range of the three groups of formulas enable the following performance of the sliding vane and the eccentric rotating assembly to be excellent, so that when the sliding vane runs to the position where the sliding vane stretches out to the shortest, the spring compression amount cannot cause the spring to break because of overlarge, and when the sliding vane runs to the position where the sliding vane stretches out to the longest, the head of the spring can always contact with the sliding vane, and the spring cannot relax and is always in a working state.
5. According to the manufacturing method of the compressor pump body, the sliding vane groove is a through groove, the tail end of the sliding vane is provided with the accommodating groove for accommodating the head end of the spring, and the following relation is adopted: lmin= (D1-D2)/2- (T1-T2); lmax= (D2-D) + (D1-D2)/2- (T1-T2); obtaining an Lmin value and an Lmax value; wherein D1 is the outer diameter of the cylinder, D2 is the inner diameter of the cylinder, D is the outer diameter of the eccentric rotating assembly, T1 is the length of the sliding sheet along the extending or retracting direction, and T2 is the groove depth of the accommodating groove. The Lmin value and the Lmax value calculated according to the formula can also be obtained through a measuring means, and the invention preferably adopts D1, D2, D, T1 and T2 with known determined values to rapidly and accurately determine the Lmin and the Lmax, thereby reducing measuring errors and improving numerical accuracy.
The present invention will be described in detail with reference to the accompanying drawings.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings that are needed in the description of the embodiments or the prior art will be briefly described, and it is obvious that the drawings in the description below are some embodiments of the present invention, and other drawings can be obtained according to the drawings without inventive effort for a person skilled in the art.
FIG. 1 is a schematic view of a pump body in embodiment 1 of the present invention;
fig. 2 is a schematic view of the structure of the cylinder in embodiment 1;
FIG. 3 is a schematic view of the structure of the roller in example 1;
FIG. 4 is a schematic structural diagram of a sliding vane in embodiment 1;
reference numerals illustrate:
1-a cylinder; 11-a sliding vane groove; 2-a spring; 3-sliding sheets; 31-a containing groove; 4-a crankshaft; 5-a roller;
in the drawing, H represents the tail groove section of the sliding vane groove, namely the hole depth of the spring, phiD 1 represents the outer diameter size of the cylinder, phiD 2 represents the inner diameter size of the cylinder, and phid represents the outer diameter size of the roller; t1 represents the length of the sliding sheet along the extending or retracting direction, and T2 represents the groove depth of the accommodating groove.
Detailed Description
The following description of the embodiments of the present invention will be made apparent and fully in view of the accompanying drawings, in which some, but not all embodiments of the invention are shown. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
In the description of the present invention, it should be noted that the directions or positional relationships indicated by the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. are based on the directions or positional relationships shown in the drawings, are merely for convenience of describing the present invention and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present invention, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present invention will be understood in specific cases by those of ordinary skill in the art.
In addition, the technical features of the different embodiments of the present invention described below may be combined with each other as long as they do not collide with each other.
Example 1
The present embodiment provides a compressor including a pump body, as shown in fig. 1 to 4, the pump body including: the cylinder 1 with the inner cavity is provided with a sliding vane groove 11 on the side wall of the inner cavity, the sliding vane groove 11 comprises two sections, namely a head groove section and a tail groove section, and the head groove section is communicated with the tail groove section. The device also comprises an eccentric rotating assembly arranged in the inner cavity of the cylinder 1, a spring 2 limited in the tail groove section, a sliding vane 3 arranged in the head groove section, and the tail of the sliding vane 3 extends into the tail groove section. The spring 2 continuously provides a biasing force to the slider 3 that keeps the head end of the slider 3 in contact with the eccentric rotating assembly as the eccentric rotating assembly rotates compressed gas along the sidewall of the inner chamber. On the basis of the structure, the spring 2 and the tail groove section of the sliding vane groove 11 for accommodating the spring 2 are respectively provided with the following characteristics: the groove depth H of the tail groove section meets the following conditions: h is more than or equal to 1.5+Lmax; the free length L0 of the spring 2 satisfies: l0 is more than or equal to 2+Lmax; the pressing height Lb of the spring 2 satisfies: lb is less than or equal to Lmin-2; where Lmin is the minimum working length of the spring 2 and Lmax is the maximum working length of the spring 2.
In addition, H satisfies H < D1-D2 in addition to H.gtoreq.1.5+Lmax.
The core technical scheme of the invention is that the springs and the processed tail groove sections are selected in the ranges of the three groups of formulas, so that when the sliding vane runs to the position where the sliding vane stretches out the shortest, the spring compression amount cannot cause the breakage of the springs due to overlarge spring, and when the sliding vane runs to the position where the sliding vane stretches out the longest, the head of the spring can always contact with the sliding vane, so that the springs cannot relax and are always in a working state, and the following performance of the sliding vane and the eccentric rotating assembly is greatly improved.
The pressing height Lb refers to the height of the spring 2 when the spring 2 is compressed to be tightly pressed in each turn. The minimum working length Lmin of the spring 2 is referred to as: when the sliding vane 3 stretches out of the sliding vane groove 2 to the shortest extent, the outer circle of the cylinder 1 is at a distance from the tail end face of the sliding vane 3. The maximum working length Lmax of the spring 2 is referred to as: when the sliding vane 3 extends out of the sliding vane groove 2 to be longest, the distance from the outer circle of the cylinder 1 to the end face of the tail end of the sliding vane 3.
Further, as shown in fig. 1 and 2, the head groove section of the sliding vane groove 11 is arranged along the axial direction of the cylinder, so that the upper end surface and the lower end surface of the sliding vane 3 can form a sealing structure with the upper flange and the lower flange of shaft seals at two ends of the cylinder, and the inner cavity is further divided into a low-pressure cavity and a high-pressure cavity, thereby realizing compressed gas. The shape and the size of the head groove section are matched with those of the sliding vane 3, so that the sliding vane 3 and the sliding vane groove 11 keep sliding sealing as much as possible when performing telescopic movement. The tail groove section of the sliding vane groove 11 is arranged in a round hole shape and is used for accommodating the spring 2.
Further, the sliding vane groove 11 is a through groove, the tail of the spring 2 is flush with the tail of the sliding vane groove 11, and the spring 2 is blocked in the sliding vane groove 11 by a blocking piece. For example, a steel plate may be disposed on the outer circle of the cylinder to seal the sliding vane groove 11, or an internal thread may be machined on the inner wall of the tail end of the sliding vane groove 11, and a bolt may be screwed with the internal thread to fix the spring 2 in the sliding vane groove 11. When the screw connection positioning is adopted, the bolt rod is provided with a groove so as to ensure that the groove bottom of the groove is flush with the outer circle of the cylinder after the screw connection positioning, and the spring is arranged in the groove on the bolt rod. So as to ensure that the tail of the spring 2 is flush with the tail end of the sliding vane groove 11, and the tail end of the sliding vane groove forms a positioning reference for measuring the groove depth H value of the tail groove section.
As an improved embodiment, as shown in fig. 4, the tail end of the sliding sheet 3 has a receiving groove 31 for receiving the head end of the spring 2. The shape of the accommodating groove 31 is matched with the shape of the head of the spring 2, for example, the accommodating groove is arranged in a conical shape or a trapezoid shape, so that the cylindrical spring and the long-strip sliding sheet can be conveniently contacted and connected.
Based on this, in the present invention, lmin and Lmax may be obtained by measurement, or may be obtained by the following formula, which is preferred in this embodiment: lmin= (D1-D2)/2- (T1-T2); lmax= (D2-D) + (D1-D2)/2- (T1-T2); wherein D1 is the outer diameter of the cylinder 1, D2 is the inner diameter of the cylinder 1, D is the outer diameter of the eccentric rotating assembly, T1 is the length of the sliding vane 3 along the extending or retracting direction, and T2 is the groove depth of the accommodating groove 31. The Lmin value and the Lmax value calculated according to the formula can also be obtained through a measuring means, and the invention preferably adopts D1, D2, D, T1 and T2 with known determined values to rapidly and accurately determine the Lmin and the Lmax, thereby reducing measuring errors and improving numerical accuracy.
In the present invention, as shown in fig. 3, the eccentric rotation assembly includes: a crankshaft 4, wherein the crankshaft 4 penetrates through the inner cavity of the cylinder 1; the roller 5 is sleeved on the crankshaft 4; the outer diameter d of the eccentric rotation assembly refers to the outer diameter of the roller 5. When the roller rotates along the inner wall of the cylinder 1, the sliding vane always moves in a telescopic way along with the roller under the action of the biasing force of the spring, and the head of the sliding vane always keeps contact with the roller.
In addition, as shown in fig. 2, the cylinder body of the cylinder 1 in the present invention has a special shape and structure, and is thickened at the place where the cylinder air inlet and the slide groove are provided, which is a conventional technical means adopted in the art, so that the outer diameter dimension of the cylinder 1 refers to the outer diameter dimension of the cylinder 1 where the slide groove 11 is located.
To better illustrate the present invention, a set of experimental data is provided to illustrate the beneficial effects of the present invention, as shown in Table 1.
Table 1:
it is apparent from examples 1-3 of the experimental data that the adoption of the calculation formula in accordance with the invention can ensure that the spring and the spring Kong Geli are valued, so that the spring is uniformly stressed and has good following property, the fatigue fracture of the spring is prevented, the reliability of the compressor is improved, abnormal sound of the compressor is avoided, and the leakage caused by the relaxation of the spring is also prevented. And the formula has simple structure and wide application range.
Example 2
The present embodiment provides a method for manufacturing a pump body of a compressor, based on the pump body in embodiment 1, including the steps of: acquiring a minimum working length Lmin value of the spring 2 and a maximum working length Lmax value of the spring 2; according to the following relation: the groove depth H of the tail groove section meets the following conditions: h is more than or equal to 1.5+Lmax; the free length L0 of the spring 2 satisfies: l0 is more than or equal to 2+Lmax; the pressing height Lb of the spring 2 satisfies: lb is less than or equal to Lmin-2; determining a groove depth H value of the tail groove section, wherein the free length L0 value of the spring 2, and the pressing height of the spring 2 is Lb value; and selecting a spring 2 according to the L0 value and the Lb value, and processing the tail groove section according to the H value. Selecting springs with Lb and L0 values meeting requirements according to the formula Lb being less than or equal to Lmin-2 and L0 being less than or equal to 2+Lmax, and processing the tail groove section H according to the formula H being less than or equal to 1.5+Lmax. The spring and the processed tail groove section selected in the range of the three groups of formulas enable the following performance of the sliding vane and the eccentric rotating assembly to be excellent, so that when the sliding vane runs to the position where the sliding vane stretches out to the shortest, the spring compression amount cannot cause the spring to break because of overlarge, and when the sliding vane runs to the position where the sliding vane stretches out to the longest, the head of the spring can always contact with the sliding vane, and the spring cannot relax and is always in a working state.
When the spring 2 is manufactured, the tail of the spring 2 is arranged flush with the tail end of the sliding vane groove 11, and the tail end of the sliding vane groove forms a positioning reference for measuring the groove depth H value of the tail groove section.
In the present invention, the slide groove 11 is a through groove, and the tail end of the slide 3 has a receiving groove 31 for receiving the head end of the spring 2, according to the following relation: lmin= (D1-D2)/2- (T1-T2); lmax= (D2-D) + (D1-D2)/2- (T1-T2); obtaining an Lmin value and an Lmax value; wherein D1 is the outer diameter of the cylinder 1, D2 is the inner diameter of the cylinder 1, D is the outer diameter of the eccentric rotating assembly, T1 is the length of the sliding vane 3 along the extending or retracting direction, and T2 is the groove depth of the accommodating groove 31. The Lmin value and the Lmax value calculated according to the formula can also be obtained through a measuring means, and the invention preferably adopts D1, D2, D, T1 and T2 with known determined values to rapidly and accurately determine the Lmin and the Lmax, thereby reducing measuring errors and improving numerical accuracy.
It is apparent that the above examples are given by way of illustration only and are not limiting of the embodiments. Other variations or modifications of the above teachings will be apparent to those of ordinary skill in the art. It is not necessary here nor is it exhaustive of all embodiments. While still being apparent from variations or modifications that may be made by those skilled in the art are within the scope of the invention.
Claims (11)
1. A compressor pump body, comprising:
the cylinder (1) is provided with an inner cavity, a sliding vane groove (11) is formed in the side wall of the inner cavity, and the sliding vane groove (11) comprises a head groove section and a tail groove section communicated with the head groove section;
the eccentric rotating assembly is arranged in the inner cavity;
a spring (2) positioned in the tail groove section;
the sliding vane (3) is arranged in the head groove section, the tail part of the sliding vane (3) extends into the tail groove section, and when the eccentric rotating assembly rotates compressed gas along the side wall of the inner cavity, the spring (2) continuously provides a biasing force for the sliding vane (3) to keep the head end of the sliding vane (3) in contact with the eccentric rotating assembly;
the groove depth H of the tail groove section meets the following conditions: h is more than or equal to 1.5+Lmax;
the free length L0 of the spring (2) satisfies the following conditions: l0 is more than or equal to 2+Lmax;
the pressing height Lb of the spring (2) is as follows: lb is less than or equal to Lmin-2;
wherein Lmin is the minimum working length of the spring (2) and Lmax is the maximum working length of the spring (2).
2. The compressor pump body according to claim 1, wherein the slide groove is a through groove, and the tail of the spring (2) is arranged flush with the tail end of the slide groove.
3. Compressor pump body according to claim 1, characterized in that the tail end of the slide (3) has a receiving groove (31) receiving the head end of the spring (2).
4. A compressor pump body according to claim 3, wherein,
Lmin＝(D1-D2)/2-(T1-T2)；
Lmax＝(D2-d)+(D1-D2)/2-(T1-T2)；
wherein D1 is the outer diameter of the cylinder (1), D2 is the inner diameter of the cylinder (1), D is the outer diameter of the eccentric rotating assembly, T1 is the length of the sliding sheet (3) along the extending or retracting direction, and T2 is the groove depth of the accommodating groove (31).
5. The compressor pump body of claim 4, wherein the eccentric rotation assembly comprises:
a crankshaft (4), wherein the crankshaft (4) penetrates through the inner cavity of the cylinder (1);
the roller (5) is sleeved on the crankshaft (4);
the outer diameter d of the eccentric rotation assembly refers to the outer diameter of the roller (5).
6. Compressor pump body according to claim 4, characterized in that the outer diameter of the cylinder (1) refers to the outer diameter of the cylinder (1) where the slide groove (11) is located.
7. The compressor pump body according to claim 2, wherein the tail end of the sliding vane groove (11) is provided with a bolt which is in threaded connection with an internal thread arranged on the inner wall of the tail end of the sliding vane groove (11).
8. Compressor, characterized by comprising a pump body according to any one of claims 1-7.
9. A method of manufacturing a compressor pump body according to any one of claims 1 to 7, comprising the steps of:
acquiring a minimum working length Lmin value of the spring (2) and a maximum working length Lmax value of the spring (2);
according to the following relation:
the groove depth H of the tail groove section meets the following conditions: h is more than or equal to 1.5+Lmax;
the free length L0 of the spring (2) satisfies the following conditions: l0 is more than or equal to 2+Lmax;
the pressing height Lb of the spring (2) is as follows: lb is less than or equal to Lmin-2;
determining a groove depth H value of the tail groove section, wherein the free length L0 value of the spring (2), and the pressing height of the spring (2) is Lb value;
and selecting a spring (2) according to the L0 value and the Lb value, and processing the tail groove section according to the H value.
10. A method of manufacturing a compressor pump body according to claim 9, wherein,
the sliding vane groove (11) is a through groove, the tail end of the sliding vane (3) is provided with a containing groove (31) for containing the head end of the spring (2), and the following relation is adopted:
Lmin＝(D1-D2)/2-(T1-T2)；
Lmax＝(D2-d)+(D1-D2)/2-(T1-T2)；
obtaining an Lmin value and an Lmax value;
wherein D1 is the outer diameter of the cylinder (1), D2 is the inner diameter of the cylinder (1), D is the outer diameter of the eccentric rotating assembly, T1 is the length of the sliding sheet (3) along the extending or retracting direction, and T2 is the groove depth of the accommodating groove (31).
11. Method for manufacturing a compressor pump body according to claim 9 or 10, characterized in that,
the tail of the spring (2) is flush with the tail end of the sliding vane groove (11), and the tail end of the sliding vane groove forms a positioning reference for measuring the groove depth H value of the tail groove section.
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| JP2001073975A (en) * | 1999-09-01 | 2001-03-21 | Matsushita Electric Ind Co Ltd | Rotary compressor |
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