CN109026699A - Pump body, compressor and pump body manufacturing method - Google Patents
Pump body, compressor and pump body manufacturing method Download PDFInfo
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- CN109026699A CN109026699A CN201810953919.0A CN201810953919A CN109026699A CN 109026699 A CN109026699 A CN 109026699A CN 201810953919 A CN201810953919 A CN 201810953919A CN 109026699 A CN109026699 A CN 109026699A
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- 238000004519 manufacturing process Methods 0.000 title claims abstract description 13
- 230000004308 accommodation Effects 0.000 claims description 17
- 238000005259 measurement Methods 0.000 claims description 10
- 238000000034 method Methods 0.000 claims description 9
- 241001391944 Commicarpus scandens Species 0.000 abstract description 2
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 230000002159 abnormal effect Effects 0.000 description 2
- 238000005096 rolling process Methods 0.000 description 2
- 206010008469 Chest discomfort Diseases 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 230000002040 relaxant effect Effects 0.000 description 1
- 238000007789 sealing 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
-
- 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 influenced because a spring of the pump body of the compressor is easy to break or loosen.
Description
Technical field
The present invention relates to rotary type compressor pump body provided therewith design fields, and in particular to a kind of pump housing, compressor and the pump housing
Manufacturing method.
Background technique
Rotary type compressor pump body provided therewith structure includes upper flange, cylinder, eccentric crankshaft, rolling-rotor, slide plate, lower flange, bullet
Spring opens up sliding vane groove on cylinder block, and spring and slide plate are located in sliding vane groove.At work, pump housing crankshaft drives rolling to compressor
The rotation of turn.Slide plate is back and forth run in sliding vane groove, and slide plate relies on the biasing force of spring, makes its head and rolling-rotor
Outer circle remains close contact, and the working chamber that cylinder and upper lower flange surround is divided into low pressure chamber and high pressure chest two parts.
Spring is the important part of rolling rotor compressor pump body, and especially for frequency-changeable compressor, revolving speed is very big
Variation in range, the stress condition of spring is very severe, and spring designing quality will have a direct impact on the reliability of compressor, such as compress
Slide plate followability when machine works has no abnormal sound and reveals, all related with spring designing quality.
In the prior art, mainly spring is designed according to gas force suffered by slide plate, the design of spring needs full
Foot is claimed below: guaranteeing that slide plate is contacted with rolling-rotor always in the process of running.But the choosing of design and spring to spring eye
A not suitable standard is selected, so that spring not only can guarantee that slide plate is contacted with rolling-rotor always in the process of running,
And guarantees that relaxation will not occur with the intensive work spring of the pump housing or be broken.In actual use, usually can
There is the pump housing to occur to be broken or biasing force cannot be generated always to slide plate and loose because spring does not tolerate the intensive work of the pump housing
It relaxes, this contingency, which causes compressor pump, to be seriously affected, or even influences its service life.
Therefore, compressor pump spring how is solved fracture or relaxation easily occurs and seriously affects compressor service life
Technical problem becomes a great problem urgently to be resolved of puzzlement those skilled in the art.
Summary of the invention
Therefore, easily occur to be broken or relax and seriously affect compressor and use the longevity the invention solves compressor pump spring
The technical issues of life, to provide the manufacturing method of a kind of pump housing, compressor and the pump housing.
For achieving the above object, the technical solution adopted by the present invention includes:
A kind of compressor pump, comprising: cylinder has inner cavity, and the side wall of the inner cavity is equipped with sliding vane groove, the slide plate
Slot includes head channel section, the tail portion slot section communicated with the head channel section；Eccentric rotary component is set in the inner cavity；Spring,
It is limited in the tail portion slot section；Slide plate is placed in the head channel section, and the tail portion of the slide plate extends to the tail portion slot
In section, when side wall of the eccentric rotary component along the inner cavity rotates compressed gas, the spring persistently mentions the slide plate
The biasing force being kept in contact for the head end and the eccentric rotary component that make the slide plate；The groove depth of the tail portion slot section
H meets: H >=1.5+Lmax；The drift L0 of the spring meets: L0 >=2+Lmax；The pressure and height of the spring are Lb
Meet: Lb≤Lmin-2；Wherein Lmin is the minimum active length of the spring, and Lmax is that the maximum functional of the spring is long
Degree.
The sliding vane groove is through slot, and the tail portion of the spring is concordant with the tail end of the sliding vane groove to be arranged.
The tail end of the slide plate has the accommodation groove (31) for the head end for accommodating the spring.
Lmin=(D1-D2)/2- (T1-T2)；Lmax=(D2-d)+(D1-D2)/2- (T1-T2)；Wherein D1 is the gas
The outer diameter of cylinder, D2 are the internal diameter of the cylinder, and d is the outer diameter of the eccentric rotary component, and T1 is the cunning
The edge of piece is stretched out or the length of retracted orientation, and T2 is the groove depth of the accommodation groove.
It include: crankshaft in the eccentric rotary component, the crankshaft runs through the inner cavity of the cylinder；Roller, the roller
It is set on the crankshaft；The outer diameter d of the eccentric rotary component refers to the outer diameter of the roller.
The outer diameter of the cylinder refers to the outer diameter of the cylinder at the sliding vane groove place.
The sliding vane groove tail end is equipped with bolt, and the internal screw thread being equipped with the inner wall of the sliding vane groove tail end is spirally connected positioning.
A kind of compressor, including according to the pump housing described above.
A kind of manufacturing method according to above-mentioned compressor pump includes the following steps: the minimum work length for obtaining spring
Spend the maximum functional length Lmax value of Lmin value and spring；According to following relational expression: the groove depth H of the tail portion slot section is full
Foot: H >=1.5+Lmax；The drift L0 of the spring meets: L0 >=2+Lmax；The pressure and height of the spring are full for Lb
Foot: Lb≤Lmin-2；Determine the groove depth H value of the tail portion slot section, the drift L0 value of the spring, the pressure of the spring
And height is Lb value；According to L0 value, Lb value chooses spring, processes the tail portion slot section according to H value.
The sliding vane groove is through slot, and the tail end of the slide plate has the accommodation groove for the head end for accommodating the spring, according to such as
Lower relational expression: Lmin=(D1-D2)/2- (T1-T2)；Lmax=(D2-d)+(D1-D2)/2- (T1-T2)；Lmin value is obtained,
Lmax value；Wherein D1 is the outer diameter of the cylinder, and D2 is the internal diameter of the cylinder, and d is the eccentric rotary component
Outer diameter, T1 be the slide plate edge stretch out or retracted orientation length, T2 be the accommodation groove groove depth.
The tail portion of the spring is concordant with the tail end of the sliding vane groove to be arranged, and the tail end of the sliding vane groove is formed described in measurement
The positioning datum of the groove depth H value of tail portion slot section.
Technical solution of the present invention has the advantages that
1. compressor pump provided by the invention, comprising: cylinder has inner cavity, and the side wall of the inner cavity is equipped with slide plate
Slot, the sliding vane groove include head channel section, the tail portion slot section communicated with the head channel section；Eccentric rotary component is set to described
In inner cavity；Spring is limited in the tail portion slot section；Slide plate is placed in the head channel section, and the tail portion of the slide plate extends
In to the tail portion slot section, when side wall of the eccentric rotary component along the inner cavity rotates compressed gas, the spring is to institute
It states slide plate and the biasing force for being kept in contact the head end of the slide plate and the eccentric rotary component is persistently provided；The tail portion
The groove depth H of slot section meets: H >=1.5+Lmax；The drift L0 of the spring meets: L0 >=2+Lmax；The spring
It presses and height is that Lb meets: Lb≤Lmin-2；Wherein Lmin is the minimum active length of the spring, and Lmax is the spring
Maximum functional length.
Above-mentioned is core of the invention technical solution, the spring chosen and the tail of processing within the scope of above-mentioned three groups of formula
Portion's slot section runs slide plate to slide plate and stretches out most in short-term, and amount of spring compression will not lead to spring breakage because of excessive, in slide plate
When operation to slide plate stretches out longest, spring head can touch slide plate always, and spring is made not relax and be in work shape always
State, so that the followability of slide plate and eccentric rotary component greatly improves.
Spring is the important spare part of compressor pump, and design requirement guarantees slide plate in the process of running in addition to meet
Always outside contacting with rolling-rotor, service life directly determines the service life of compressor pump.But in the prior art, spring is set
Although meter can satisfy in initialization followability requirement, with the intensive work of compressor pump, usually due to
Spring easily occurs to be broken or relax and gas leakage or even cisco unity malfunction occurs, and influences the service life of compressor.Cause
How this, guarantee that spring still can continue permanent efficient work under severe stress condition, i.e., when working under high stress not
It is not easy to relax when easy fracture, intensive work, this just puts forward new requirements the design of spring.The present invention is exactly directed to above-mentioned
It is required that and devise a kind of new compressor pump, so that the relative dimensions of spring and compressor pump component is met certain design and want
It asks, that is, is not easy to relax when can guarantee spring not easy to break when working under high stress, intensive work, substantially prolongs spring
Service life, and then extend the service life of compressor pump.
2. compressor pump provided by the invention, the tail end of the slide plate has the accommodation groove for the head end for accommodating the spring
(31), Lmin=(D1-D2)/2- (T1-T2)；Lmax=(D2-d)+(D1-D2)/2- (T1-T2)；Wherein D1 is the cylinder
Outer diameter, D2 be the cylinder internal diameter, d be the eccentric rotary component outer diameter, T1 be the slide plate
Edge stretch out or retracted orientation length, T2 be the accommodation groove groove depth.The Lmin value being calculated according to above-mentioned formula
With Lmax value, Lmin the and Lmax value of spring can also be obtained by measurement means, present invention preferably employs by with known true
D1, D2, d, T1, T2 of fixed number value fast and accurately determine Lmin and Lmax, reduce measurement error, improve numerical precision.
3. compressor provided by the invention, including according to the pump housing described above.Have the advantages that all of the above-mentioned pump housing.
4. the manufacturing method of compressor pump provided by the invention includes the following steps: the minimum work length for obtaining spring
Spend the maximum functional length Lmax value of Lmin value and spring；According to following relational expression: the groove depth H of the tail portion slot section is full
Foot: H >=1.5+Lmax；The drift L0 of the spring meets: L0 >=2+Lmax；The pressure and height of the spring are full for Lb
Foot: Lb≤Lmin-2；Determine the groove depth H value of the tail portion slot section, the drift L0 value of the spring, the pressure of the spring
And height is Lb value；According to L0 value, Lb value chooses spring, processes the tail portion slot section according to H value.According to above-mentioned formula Lb≤
Lmin-2, L0 >=2+Lmax process to choose the satisfactory spring of Lb, L0 numerical value, and according to formula H >=1.5+Lmax
Tail portion slot section H.The spring chosen and the tail portion slot section of processing within the scope of above-mentioned three groups of formula, so that slide plate and eccentric rotary
The followability of component is fabulous, makes to run in slide plate to slide plate and stretch out most in short-term, amount of spring compression will not lead to bullet because of excessive
Spring fracture, when slide plate runs and stretches out longest to slide plate, spring head can touch slide plate always, and spring is made not relax and begin
It is in running order eventually.
5. the manufacturing method of compressor pump provided by the invention, the sliding vane groove is through slot, and the tail end of the slide plate has
There is the accommodation groove for the head end for accommodating the spring, according to following relational expression: Lmin=(D1-D2)/2- (T1-T2)；Lmax=
(D2-d)+(D1-D2)/2-(T1-T2)；Obtain Lmin value, Lmax value；Wherein D1 is the outer diameter of the cylinder, and D2 is institute
The internal diameter of cylinder is stated, d is the outer diameter of the eccentric rotary component, and T1 is edge stretching or the retracted orientation of the slide plate
Length, T2 be the accommodation groove groove depth.The Lmin value and Lmax value being calculated according to above-mentioned formula, can also pass through survey
Amount means obtain Lmin the and Lmax value of spring, present invention preferably employs by D1, D2 with known determining numerical value, d, T1,
T2 fast and accurately determines Lmin and Lmax, reduces measurement error, improves numerical precision.
The present invention is described in detail with reference to the accompanying drawing.
Detailed description of the invention
It, below will be to specific in order to illustrate more clearly of the specific embodiment of the invention or technical solution in the prior art
Embodiment or attached drawing needed to be used in the description of the prior art be briefly described, it should be apparent that, it is described below
Attached drawing is some embodiments of the present invention, for those of ordinary skill in the art, before not making the creative labor
It puts, is also possible to obtain other drawings based on these drawings.
Fig. 1 is the structural schematic diagram of 1 middle pump body of the embodiment of the present invention；
Fig. 2 is the structural schematic diagram of cylinder in embodiment 1；
Fig. 3 is the structural schematic diagram of roller in embodiment 1；
Fig. 4 is the structural schematic diagram of slide plate in embodiment 1；
Description of symbols:
1- cylinder；11- sliding vane groove；2- spring；3- slide plate；31- accommodation groove；4- crankshaft；5- roller；
H indicates the tail portion slot section of sliding vane groove, i.e. spring eye hole depth in attached drawing, and φ D1 indicates the outer diameter of cylinder, φ D2
Indicate the internal diameter of cylinder, φ d indicates the outer diameter of roller；T1 indicates the edge stretching or the length of retracted orientation of the slide plate
Degree, T2 indicate the groove depth of accommodation groove.
Specific embodiment
Technical solution of the present invention is clearly and completely described below in conjunction with attached drawing, it is clear that described implementation
Example is a part of the embodiment of the present invention, instead of all the embodiments.Based on the embodiments of the present invention, ordinary skill
Personnel's every other embodiment obtained without making creative work, shall fall within the protection scope of the present invention.
In the description of the present invention, it should be noted that term " center ", "upper", "lower", "left", "right", "vertical",
The orientation or positional relationship of the instructions such as "horizontal", "inner", "outside" be based on the orientation or positional relationship shown in the drawings, merely to
Convenient for description the present invention and simplify description, rather than the device or element of indication or suggestion meaning must have a particular orientation,
It is constructed and operated in a specific orientation, therefore is not considered as limiting the invention.In addition, term " first ", " second ",
" third " is used for descriptive purposes only and cannot be understood as indicating or suggesting relative importance.
In the description of the present invention, it should be noted that unless otherwise clearly defined and limited, term " installation ", " phase
Even ", " connection " shall be understood in a broad sense, for example, it may be being fixedly connected, may be a detachable connection, or be integrally connected；It can
To be mechanical connection, it is also possible to be electrically connected；It can be directly connected, can also can be indirectly connected through an intermediary
Connection inside two elements.For the ordinary skill in the art, above-mentioned term can be understood at this with concrete condition
Concrete meaning in invention.
As long as in addition, the non-structure each other of technical characteristic involved in invention described below different embodiments
It can be combined with each other at conflict.
Embodiment 1
The present embodiment provides a kind of compressors, including the pump housing, and as shown in Figs 1-4, the pump housing includes: the gas with inner cavity
Cylinder 1, the side wall of the inner cavity are equipped with sliding vane groove 11, and the sliding vane groove 11 includes two sections, i.e. head channel section and tail portion slot section, head
Portion's slot section is communicated with tail portion slot section.Further include the eccentric rotary component in the inner cavity of the cylinder 1, is limited in the tail portion
Spring 2 in slot section, the slide plate 3 being placed in the head channel section, and the tail portion of the slide plate 3 extends to the tail portion slot section
It is interior.When side wall of the eccentric rotary component along the inner cavity rotates compressed gas, the spring 2 continues the slide plate 3
The biasing force for being kept in contact the head end of the slide plate 3 and the eccentric rotary component is provided.On the basis of the said structure,
The tail portion slot section of the sliding vane groove 11 of spring 2 and putting spring 2, is respectively provided with following feature: the groove depth H of the tail portion slot section is full
Foot: H >=1.5+Lmax；The drift L0 of the spring 2 meets: L0 >=2+Lmax；The pressure and height of the spring 2 are full for Lb
Foot: Lb≤Lmin-2；Wherein Lmin is the minimum active length of the spring 2, and Lmax is that the maximum functional of the spring 2 is long
Degree.
In addition, H in addition to H >=1.5+Lmax to be met, will also meet H < D1-D2.
Above-mentioned is the core of the invention technical solution spring chosen and tail of processing within the scope of above-mentioned three groups of formula
Portion's slot section runs slide plate to slide plate and stretches out most in short-term, and amount of spring compression will not lead to spring breakage because of excessive, in slide plate
When operation to slide plate stretches out longest, spring head can touch slide plate always, and spring is made not relax and be in work shape always
State, so that the followability of slide plate and eccentric rotary component greatly improves.
Wherein, the height of above-mentioned pressure and height Lb are referred to when spring 2 is compressed to each circle all and is tight spring 2.It is described
The minimum active length Lmin of spring 2 is referred to: when the slide plate 3 stretches out the sliding vane groove 2 most in short-term, outside the cylinder 1
Distance of the circle to the tail end end face of slide plate 3.The maximum functional length Lmax of the spring 2 is referred to: when the slide plate 3 stretches out institute
When stating 2 longest of sliding vane groove, the distance of the outer circle of the cylinder 1 to the tail end end face of slide plate 3.
It further illustrates, as illustrated in fig. 1 and 2, the head channel section of sliding vane groove 11 axially penetrates through setting along cylinder, so that slide plate
3 upper and lower end face can form sealing structure with the upper lower flange of cylinder both ends axle envelope, and then inner cavity is divided into low pressure chamber and height
Chamber is pressed, realizes compressed gas.Head channel section and the shape and size of slide plate 3 match, to guarantee that slide plate 3 is carrying out stretching motion
When, it keeps being slidingly sealed as far as possible with sliding vane groove 11.The tail portion slot section of sliding vane groove 11 is set as circular hole, is used for putting spring 2.
It further illustrates, the sliding vane groove 11 is through slot, and the tail portion of the spring 2 is concordant with the tail end of the sliding vane groove 11
Setting, and blocked spring 2 in sliding vane groove 11 using closeouts.Steel plate is set in cylinder outer circle to institute for example, can be used
Sliding vane groove 11 is stated to be blocked, it can also be using 11 tail end inwall processing of sliding vane groove be gone out internal screw thread, using bolt and internal screw thread
The positioning that is spirally connected blocks spring 2 in sliding vane groove 11.Using be spirally connected position when, groove is set on shank of bolt, it is fixed to guarantee to be spirally connected
Position rearward recess slot bottom is flushed with cylinder outer circle, and spring is placed in the groove on shank of bolt.To guarantee tail portion and the institute of the spring 2
The tail end for stating sliding vane groove 11 is concordantly arranged, and the tail end of the sliding vane groove is made to form the groove depth H value for measuring the tail portion slot section
Positioning datum.
As embodiment is improved, as shown in figure 4, the tail end of the slide plate 3 has the accommodating for the head end for accommodating the spring 2
Slot 31.The shape of accommodation groove 31 and the head shape of spring 2 match, for example, be respectively provided with it is tapered or trapezoidal, to facilitate circle
Column spring is connected with strip slide plate.
Based on this, in the present invention, the mode that measurement can be used in Lmin and Lmax is obtained, and following formula can also be used and obtain,
The present embodiment is preferably obtained using following formula: Lmin=(D1-D2)/2- (T1-T2)；Lmax=(D2-d)+(D1-D2)/2-
(T1-T2)；Wherein D1 is the outer diameter of the cylinder 1, and D2 is the internal diameter of the cylinder 1, and d is the eccentric rotary group
The outer diameter of part, T1 are that the edge of the slide plate 3 is stretched out or the length of retracted orientation, T2 are the groove depth of the accommodation groove 31.
The Lmin value and Lmax value being calculated according to above-mentioned formula, can also obtain Lmin the and Lmax value of spring by measurement means,
Present invention preferably employs fast and accurately determining Lmin and Lmax by D1, D2, d, T1, T2 with known determining numerical value,
Measurement error is reduced, numerical precision is improved.
In the present invention, the eccentric rotary component is as shown in Figure 3, comprising: crankshaft 4, the crankshaft 4 run through the cylinder 1
Inner cavity；Roller 5, the roller 5 are set on the crankshaft 4；The outer diameter d of the eccentric rotary component refers to described
The outer diameter of roller 5.For roller when along the rotation of 1 inner wall of cylinder, slide plate follows roller under the partial pressure of spring always
Stretching motion is done, the head of slide plate is kept in contact with roller always.
In addition, as shown in Fig. 2, its outer circular shape of the cylinder body of cylinder 1 and structure in the present invention are special, in cylinder air inlet
It is thickeied with the place of sliding vane groove setting, this is the conventional technical means that this field uses, therefore, outside the cylinder 1
Diameter size refers to the outer diameter of the cylinder 1 where the sliding vane groove 11.
To better illustrate the present invention, one group of experimental data is provided for illustrating beneficial effects of the present invention, such as 1 institute of table
Show.
Table 1:
It is not difficult to find out by the embodiment 1-3 of above-mentioned experimental data, using calculation formula in the present invention is met, to spring and bullet
Spring hole reasonable value, it is ensured that spring stress is uniform, and followability is good, and spring fatigue is prevented to be broken, and improves compressor reliability, keeps away
Exempt from compressor abnormal sound, is also prevented from relaxing of spring and leaks.And formula structure is simple, it is applied widely.
Embodiment 2
The present embodiment provides a kind of manufacturing methods of compressor pump, walk based on the pump housing in embodiment 1, including as follows
It is rapid: to obtain the maximum functional length Lmax value of the minimum active length Lmin value and spring 2 of spring 2；According to following relationship
Formula: the groove depth H of the tail portion slot section meets: H >=1.5+Lmax；The drift L0 of the spring 2 meets: L0 >=2+
Lmax；The pressure and height of the spring 2 are that Lb meets: Lb≤Lmin-2；Determine the groove depth H value of the tail portion slot section, it is described
The drift L0 value of spring 2, the pressure and height of the spring 2 are Lb value；According to L0 value, Lb value chooses spring 2, according to H value
Process the tail portion slot section.The satisfactory bullet of Lb, L0 numerical value is chosen according to above-mentioned formula Lb≤Lmin-2, L0 >=2+Lmax
Spring, and tail portion slot section H is processed according to formula H >=1.5+Lmax.The spring chosen within the scope of above-mentioned three groups of formula and
The tail portion slot section of processing makes to run in slide plate most short to slide plate stretching so that the followability of slide plate and eccentric rotary component is fabulous
When, amount of spring compression will not lead to spring breakage because of excessive, when slide plate runs and stretches out longest to slide plate, spring head energy
Always slide plate is touched, so that spring is not relaxed and in running order always.
When carrying out above-mentioned processing and manufacturing, make the tail portion of spring 2 is concordant with the tail end of the sliding vane groove 11 to be arranged, the cunning
The tail end of film trap forms the positioning datum for measuring the groove depth H value of the tail portion slot section.
In the present invention, sliding vane groove 11 is through slot, and the tail end of the slide plate 3 has the accommodating for the head end for accommodating the spring 2
Slot 31, according to following relational expression: Lmin=(D1-D2)/2- (T1-T2)；Lmax=(D2-d)+(D1-D2)/2- (T1-T2)；It obtains
Take Lmin value, Lmax value；Wherein D1 is the outer diameter of the cylinder 1, and D2 is the internal diameter of the cylinder 1, and d is described inclined
The outer diameter of heart runner assembly, T1 are that the edge of the slide plate 3 is stretched out or the length of retracted orientation, T2 are the accommodation groove 31
Groove depth.The Lmin value and Lmax value being calculated according to above-mentioned formula, can also be obtained by measurement means spring Lmin and
Lmax value, present invention preferably employs fast and accurately determine Lmin by D1, D2, d, T1, T2 with known determining numerical value
And Lmax, measurement error is reduced, numerical precision is improved.
Obviously, the above embodiments are merely examples for clarifying the description, and does not limit the embodiments.It is right
For those of ordinary skill in the art, can also make on the basis of the above description it is other it is various forms of variation or
It changes.There is no necessity and possibility to exhaust all the enbodiments.And it is extended from this it is obvious variation or
It changes still within the protection scope of the invention.
Claims (11)
1. a kind of compressor pump characterized by comprising
Cylinder (1) has inner cavity, and the side wall of the inner cavity is equipped with sliding vane groove (11), and the sliding vane groove (11) includes head channel
Section, the tail portion slot section communicated with the head channel section；
Eccentric rotary component is set in the inner cavity；
Spring (2) is limited in the tail portion slot section；
Slide plate (3) is placed in the head channel section, and the tail portion of the slide plate (3) extends in the tail portion slot section, described inclined
When side wall of the heart runner assembly along the inner cavity rotates compressed gas, the spring (2), which persistently provides the slide plate (3), makes institute
State the head end of slide plate (3) and biasing force that the eccentric rotary component is kept in contact；
The groove depth H of the tail portion slot section meets: H >=1.5+Lmax；
The drift L0 of the spring (2) meets: L0 >=2+Lmax；
The pressure and height of the spring (2) are that Lb meets: Lb≤Lmin-2；
Wherein Lmin is the minimum active length of the spring (2), and Lmax is the maximum functional length of the spring (2).
2. compressor pump according to claim 1, which is characterized in that the sliding vane groove is through slot, the spring (2)
Tail portion is concordant with the tail end of the sliding vane groove to be arranged.
3. compressor pump according to claim 1, which is characterized in that the tail end of the slide plate (3) has described in accommodating
The accommodation groove (31) of the head end of spring (2).
4. compressor pump according to claim 3, which is characterized in that
Lmin=(D1-D2)/2- (T1-T2)；
Lmax=(D2-d)+(D1-D2)/2- (T1-T2)；
Wherein D1 is the outer diameter of the cylinder (1), and D2 is the internal diameter of the cylinder (1), and d is the eccentric rotary group
The outer diameter of part, T1 are that the edge of the slide plate (3) is stretched out or the length of retracted orientation, T2 are the groove depth of the accommodation groove (31)
Degree.
5. compressor pump according to claim 4, which is characterized in that include: in the eccentric rotary component
Crankshaft (4), the crankshaft (4) run through the inner cavity of the cylinder (1)；
Roller (5), the roller (5) are set on the crankshaft (4)；
The outer diameter d of the eccentric rotary component refers to the outer diameter of the roller (5).
6. compressor pump according to claim 1, which is characterized in that the outer diameter of the cylinder (1) refers to institute
State the outer diameter of the cylinder (1) at sliding vane groove (11) place.
7. compressor pump according to claim 2, which is characterized in that sliding vane groove (11) tail end is equipped with bolt, with
The internal screw thread that the inner wall of sliding vane groove (11) tail end is equipped with is spirally connected positioning.
8. a kind of compressor, which is characterized in that including the pump housing according to claim 1-7.
9. a kind of manufacturing method of such as compressor pump of any of claims 1-7, which is characterized in that including as follows
Step:
Obtain the minimum active length Lmin value of spring (2) and the maximum functional length Lmax value of spring (2)；
According to following relational expression:
The groove depth H of the tail portion slot section meets: H >=1.5+Lmax；
The drift L0 of the spring (2) meets: L0 >=2+Lmax；
The pressure and height of the spring (2) are that Lb meets: Lb≤Lmin-2；
Determine the groove depth H value of the tail portion slot section, the drift L0 value of the spring (2), the pressure and height of the spring (2)
Degree is Lb value；
According to L0 value, Lb value chooses spring (2), processes the tail portion slot section according to H value.
10. the manufacturing method of compressor pump according to claim 9, which is characterized in that
The sliding vane groove (11) is through slot, and the tail end of the slide plate (3) has the accommodation groove for the head end for accommodating the spring (2)
(31), according to following relational expression:
Lmin=(D1-D2)/2- (T1-T2)；
Lmax=(D2-d)+(D1-D2)/2- (T1-T2)；
Obtain Lmin value, Lmax value；
Wherein D1 is the outer diameter of the cylinder (1), and D2 is the internal diameter of the cylinder (1), and d is the eccentric rotary group
The outer diameter of part, T1 are that the edge of the slide plate (3) is stretched out or the length of retracted orientation, T2 are the groove depth of the accommodation groove (31)
Degree.
11. the manufacturing method of compressor pump according to claim 9 or 10, which is characterized in that
The tail portion of the spring (2) is concordant with the tail end of the sliding vane groove (11) to be arranged, and the tail end of the sliding vane groove forms measurement
The positioning datum of the groove depth H value of the tail portion slot section.
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| CN201810953919.0A CN109026699B (en) | 2018-08-21 | 2018-08-21 | Pump body, compressor and manufacturing method of pump body |
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| CN201810953919.0A CN109026699B (en) | 2018-08-21 | 2018-08-21 | Pump body, compressor and manufacturing method of pump body |
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| CN109026699B CN109026699B (en) | 2024-03-29 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112483395A (en) * | 2020-11-18 | 2021-03-12 | 安徽名杰磁业科技有限公司 | Compressor rotor assembly and production method thereof |
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| CN1692228A (en) * | 2002-12-11 | 2005-11-02 | 松下电器产业株式会社 | Rotary compressor |
| CN107503940A (en) * | 2017-09-14 | 2017-12-22 | 珠海格力电器股份有限公司 | Pump body assembly, fluid machine and heat exchange equipment |
| CN208763896U (en) * | 2018-08-21 | 2019-04-19 | 珠海凌达压缩机有限公司 | Pump body and compressor |
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2018
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|---|---|---|---|---|
| JPH10274184A (en) * | 1997-03-31 | 1998-10-13 | Toshiba Corp | Rotary compressor |
| JP2001073975A (en) * | 1999-09-01 | 2001-03-21 | Matsushita Electric Ind Co Ltd | Rotary compressor |
| JP2001280276A (en) * | 2000-03-30 | 2001-10-10 | Sanyo Electric Co Ltd | Multistage compressor |
| CN1692228A (en) * | 2002-12-11 | 2005-11-02 | 松下电器产业株式会社 | Rotary compressor |
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| CN112483395A (en) * | 2020-11-18 | 2021-03-12 | 安徽名杰磁业科技有限公司 | Compressor rotor assembly and production method thereof |
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| CN109026699B (en) | 2024-03-29 |
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