CN101413495B - Suction structure in double-headed piston type compressor - Google Patents
Suction structure in double-headed piston type compressor Download PDFInfo
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- CN101413495B CN101413495B CN2008101660535A CN200810166053A CN101413495B CN 101413495 B CN101413495 B CN 101413495B CN 2008101660535 A CN2008101660535 A CN 2008101660535A CN 200810166053 A CN200810166053 A CN 200810166053A CN 101413495 B CN101413495 B CN 101413495B
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- communication passage
- guiding channel
- pressing chamber
- diameter
- double
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1009—Distribution members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B25/00—Multi-stage pumps
- F04B25/04—Multi-stage pumps having cylinders coaxial with, or parallel or inclined to, main shaft axis
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/10—Adaptations or arrangements of distribution members
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
The invention relates to a suction structure in double-headed piston type compressor, specifically to a suction structure, which is provided for allowing refrigerant into first and second compression chambers from a suction pressure region through first and second rotary valves and first and second communication passages in a double-headed piston type compressor. The first and the second rotary valves respectively have first and second introduction passages. The distance to the first communication passage from the suction pressure region through the first introduction passage is greater than the distance to the second communication passage from the suction pressure region through the second introduction passage. The first communication passage with a circular cross-section in the cylinder block connects the first compression chamber to the first introduction passage. The second communication passage with a circular cross-section in the cylinder block connects the second compression chamber to the second introduction passage. The diameter of the first communication passage is greater than the diameter of the second communication passage.
Description
Technical field
The present invention relates to a kind of suction structure that is used for entering from the suction pressure district pressing chamber at double-headed piston type compressor permission freezing mixture.More particularly, this compressor has the rotary valve that rotates with running shaft with being integral, and this rotary valve has guiding channel so that freezing mixture is introduced from the suction pressure district by the pressing chamber of double-head piston defined in the cylinder thorax (bores).
Background technique
In double-headed piston type compressor, there is two types suction valve.A kind of is as disclosed rotary valve among the uncensored Japanese patent publication No.2007-032445.Another kind is as disclosed reed-type suction valve among the uncensored Japanese patent publication No.2000-145629.Compare with the piston compressor that comprises the reed-type suction valve, comprise that the piston compressor of rotary valve has lower suction resistance when freezing mixture is introduced the cylinder thorax, and have higher energy efficiency.
In the disclosed compressor, paired preceding cylinder thorax and back cylinder thorax accommodate double-head piston therein, and this piston is reciprocating along with the rotation of running shaft in above reference No.2007-032445.Each double-head piston limits preceding pressing chamber in preceding cylinder thorax, and limits the back pressing chamber in the cylinder thorax of back.This running shaft has preceding rotary valve and the back rotary valve that is integrally formed therewith.Service duct is formed in this running shaft, and the outlet of this service duct is formed in preceding rotary valve and the back rotary valve.Communication passage is formed in the cylinder body, so that be communicated with pressing chamber.The outlet of this service duct intermittently is communicated with communication passage along with the rotation of running shaft or along with the rotation of rotary valve.When the outlet of service duct was communicated with communication passage, the freezing mixture in this service duct was introduced into pressing chamber.
Usually, communication passage has elongated cross section, as disclosed in uncensored Japanese patent publication No.6-129350.Elongated hole form by this way so that the size of this elongated hole on the axial direction of running shaft greater than its size on circumferential direction.Using elongated hole is in order to collect the residual gas in the pressing chamber, to improve volumetric efficiency thus.
Service duct is communicated with suction chamber in being formed on rear case, so that pressing chamber and back pressing chamber before via this service duct the freezing mixture in the suction chamber being supplied to.By pushing corresponding expulsion valve open, the freezing mixture in the preceding pressing chamber is discharged in the preceding discharge chamber that is formed in the front case.By pushing corresponding expulsion valve open, the freezing mixture in the back pressing chamber is discharged in the back discharge chamber that is formed in the rear case.
Preceding pressure of discharging in the chamber equals the pressure in the discharge chamber, back.Freezing mixture in the pressing chamber is compressed to the stress level in discharging the chamber.Therefore, when the amount of the freezing mixture in introducing pressing chamber reduced, compressibility raise.When compressibility raise, the temperature of freezing mixture by compression correspondingly raise.
From suction chamber via service duct to the distance of preceding pressing chamber greater than from suction chamber via the distance of this service duct to the back pressing chamber.Therefore, in the period when communication passage is communicated with the outlet of rotary valve respectively, the amount of the freezing mixture before entering in the pressing chamber is less than the amount that enters the freezing mixture in the pressing chamber of back.The temperature of the freezing mixture that compresses in preceding pressing chamber correspondingly becomes and be higher than the temperature of the freezing mixture that compresses in the pressing chamber of back.
When the temperature of the freezing mixture that compresses in preceding pressing chamber became too high, the temperature of front case raise.Place the sealing function of the sealed member between front case and the cylinder body correspondingly to worsen.
The temperature that the objective of the invention is to be suppressed in the pressing chamber of double-headed piston type compressor freezing mixture by compression raises.
Summary of the invention
According to the present invention, provide a kind of suction structure, so that in double-headed piston type compressor, allow freezing mixture to enter pressing chamber from the suction pressure district.This compressor has cylinder body, running shaft, double-head piston, the first cylinder thorax and the second cylinder thorax, and first pressing chamber and second pressing chamber.This running shaft is supported by cylinder body.This double-head piston is reciprocating along with the rotation of running shaft.This first cylinder thorax and the second cylinder thorax are formed in the cylinder body in paired mode, so that hold double-head piston.This first pressing chamber and second pressing chamber are limited in the first cylinder thorax and the second cylinder thorax by double-head piston respectively.Suction structure in this compressor comprises first rotary valve and second rotary valve, and first communication passage and second communication passage.This first rotary valve is introduced first pressing chamber with freezing mixture from the suction pressure district via first guiding channel.This second rotary valve is introduced second pressing chamber with freezing mixture from the suction pressure district via second guiding channel.Each several part in this first guiding channel and second guiding channel all is formed in the running shaft.This first communication passage has circular cross-section and is formed in the cylinder body, so that first pressing chamber is connected on first guiding channel.This second communication passage has circular cross-section and is formed in the cylinder body, so that second pressing chamber is connected on second guiding channel.From the suction pressure district via first guiding channel to the distance of first communication passage greater than from this suction pressure district via the distance of second guiding channel to second communication passage.The diameter of this first communication passage is greater than the diameter of this second communication passage.
According in conjunction with the accompanying drawings and the following description by the by way of example explanation principle of the invention, other aspects and advantages of the present invention will become apparent.
Description of drawings
The present invention is considered as novel characteristics and has carried out setting forth particularly in claims.By the reference currently preferred embodiments also in conjunction with the accompanying drawings, can understand the present invention and purpose and advantage better, in the accompanying drawing:
Fig. 1 is the longitdinal cross-section diagram of compressor according to the preferred embodiment of the invention;
Fig. 2 A is the local amplification sectional view according to the compressor of preferred embodiment;
Fig. 2 B is the sectional view that the III-III line in Fig. 2 A is intercepted;
Fig. 2 C is the sectional view that the IV-IV line in Fig. 2 A is intercepted;
Fig. 2 D is the plotted curve according to preferred embodiment, discharges the relation between the section ratio of temperature and the relevant first communication passage area and the second communication passage area in the chamber before its expression;
Fig. 3 A is the sectional view that the I-I line in Fig. 1 is intercepted; And
Fig. 3 B is the sectional view that the II-II line in Fig. 1 is intercepted.
Embodiment
Preferred embodiment according to double-headed piston type compressor 10 of the present invention is described with reference to Fig. 1 to Fig. 3.What notice is that the front side of double-headed piston type compressor 10 and rear side correspond respectively to left side and the right side among the figure.In addition, the front side of compressor 10 and rear side are respectively as first side and second side.With reference to Fig. 1, front-bank rotor housing 11 is attached on the rear-bank rotor housing 12.Front case 13 is attached on the front-bank rotor housing 11.Rear case 14 is attached on the rear-bank rotor housing 12.Front and back cylinder body 11,12 and front and back housing 13,14 constitute the whole frame set of double-headed piston type compressors 10.Preceding discharge chamber 131 as the head pressure district in the compressor 10 is limited in the front case 13.Back discharge chamber 141 as the head pressure district in the compressor 10 is limited in the rear case 14.Suction chamber 142 as the suction pressure district is limited in the rear case 14.Should be noted that " in compressor " inside corresponding to the whole compressor frame set of compressor 10, " outside compressor " is then corresponding to the outside of whole compressor frame set.
Valve port plate 15, valve plate 16 and retainer plate 17 place between front-bank rotor housing 11 and the front case 13.Valve port plate 18, valve plate 19 and retainer plate 20 place between rear-bank rotor housing 12 and the rear case 14.Exhaust port 151,181 is respectively formed in the valve port plate 15,18.Expulsion valve 161,191 is respectively formed in the valve plate 16,19, with the corresponding exhaust port 151,181 of opening and closing.Retainer 171,201 is respectively formed in the retainer plate 17,20, to regulate the open degree of corresponding expulsion valve 161,191.
Before and after not shown liner is placed at respectively between the cylinder body 11,12, between front-bank rotor housing 11 and the front case 13, and between rear-bank rotor housing 12 and the rear case 14.Liner is made by sheet metal, and wherein the surface of sheet metal both sides is covered by rubber sealant.This liner is used for preventing that coolant gas is via between the front and back cylinder body 11,12, between front-bank rotor housing 11 and the front case 13 and the clearance leakage between rear-bank rotor housing 12 and the rear case 14.
Running shaft 21 is rotatably mounted by front and back cylinder body 11,12, and inserts in the axis hole 111,121 that extends via front and back cylinder body 11,12.The inner circumference contact of the excircle of running shaft 21 and axis hole 111,121.Running shaft 21 is directly supported by front and back cylinder body 11,12 via the inner circumference of corresponding axis hole 111,121.The contact segment of the excircle of running shaft 21 and axis hole 111 forms sealing peripheral surface 211.The contact segment of the excircle of running shaft 21 and axis hole 121 forms sealing peripheral surface 212.
Wobbler 23 as cam body is fastened on the running shaft 21.In the crankshaft room 24 before and after wobbler 23 is contained in and is limited between the cylinder body 11,12.Lip seal formula shaft sealing part 22 places between front case 13 and the running shaft 21.Shaft sealing part 22 can prevent that coolant gas is via the clearance leakage between front case 13 and the running shaft 21.Be connected on the vehicle motor 26 of driving source outside the conduct by magnetic clutch 25 from the front end of front case 13 outwardly directed running shafts 21.Running shaft 21 receives the driving force that is used to rotate by magnetic clutch 25 from vehicle motor 26.
As shown in Fig. 3 A, a plurality of first cylinder thoraxes 27 are formed in the front-bank rotor housing 11, and arrange around running shaft 21.As shown in Fig. 3 B, a plurality of second cylinder thoraxes 28 are formed in the rear-bank rotor housing 12, and arrange around running shaft 21.Double-head piston 29 is contained in each in the cylinder thorax 27,28.
As shown in fig. 1, double-head piston 29 engages with wobbler 23 by a pair of cushion block (shoes) 30.Wobbler 23 rotates with running shaft 21 with being integral.Rotatablely moving of wobbler 23 is transferred to double-head piston 29 by cushion block 30, so that each double-head piston 29 is reciprocating in to 27,28 at corresponding cylinder thorax.Each double-head piston 29 has columned first head 291, and it defines first pressing chamber 271 in the corresponding first cylinder thorax 27.Each double-head piston 29 has columned second head 292 in the end opposite of first head 291, and this second head 292 defines second pressing chamber 281 in the corresponding second cylinder thorax 28.
Axle internal channel 31 is formed in the running shaft 21.Axle internal channel 31 extends along the spin axis 210 of running shaft 21.The suction chamber 142 in the rear case 14 is led in the import 311 of axle internal channel 31.Preceding sealing peripheral surface 211 places of the running shaft 21 of first outlet 312 in axis hole 111 of axle internal channel 31 open.Back sealing peripheral surface 212 places of the running shaft 21 of second outlet 313 in axis hole 121 of axle internal channel 31 open.
Shown in Fig. 2 A and Fig. 3 A, first communication passage 32 is formed in the front-bank rotor housing 11, so that be communicated with the first cylinder thorax 27 and axis hole 111.Shown in Fig. 2 B and Fig. 3 B, second communication passage 33 is formed in the rear-bank rotor housing 12, so that be communicated with the second cylinder thorax 28 and axis hole 121.When running shaft 21 rotated, first outlet, 312 and second outlet 313 of axle internal channel 31 intermittently was communicated with first communication passage 32 and second communication passage 33 respectively.
When one of them first cylinder thorax 27 was in the suction process, when just being in the process that the left side of double-head piston 29 from Fig. 1 move to the right side, first outlet 312 was communicated with first communication passage 32.As a result, the freezing mixture in the suction chamber 142 is introduced in first pressing chamber 271 of the first cylinder thorax 27 by axle internal channel 31, first outlet, 312 and first communication passage 32.
When the first cylinder thorax 27 was in the discharge process, when promptly being in the process that the right side of double-head piston 29 from Fig. 1 move to the left side, first connection of outlet between 312 and first communication passage 32 was closed.As a result, the refrigeration agent in first pressing chamber 271 is discharged in the chamber 131 before expulsion valve 161 is discharged to via exhaust port 151 by pushing open.Being discharged to the freezing mixture of discharging in the chamber 131 flows out in the outer coolant circuit 34 via passage 341.
When one of them second cylinder thorax 28 was in the suction process, when just being in the process that the right side of double-head piston 29 from Fig. 1 move to the left side, second outlet 313 was communicated with second communication passage 33.As a result, the freezing mixture in the suction chamber 142 is introduced in second pressing chamber 281 of the second cylinder thorax 28 via axle internal channel 31, second outlet, 313 and second communication passage 33.
When the second cylinder thorax 28 was in the discharge process, when just being in the process that the left side of double-head piston 29 from Fig. 1 move to the right side, being communicated with between second outlet 313 and second communication passage 33 was closed.As a result, the refrigeration agent in second pressing chamber 281 is discharged in the discharge chamber 141, back via exhaust port 181 by pushing expulsion valve 191 open.Being discharged to the freezing mixture of discharging in the chamber 141 flows out in the outer coolant circuit 34 via passage 342.
Part corresponding to sealing peripheral surface 211 in the running shaft 21 has formed first rotary valve 35.Part corresponding to sealing peripheral surface 212 in the running shaft 21 has formed second rotary valve 36. Rotary valve 35,36 is integrally formed into running shaft 21.The axle internal channel 31 and first outlet 312 are formed for first guiding channel 40 of rotary valve 35.The axle internal channel 31 and second outlet 313 are formed for second guiding channel 41 of rotary valve 36.The part of shared first guiding channel 40 of the part of second guiding channel 41 in running shaft 21.The length of first guiding channel 40 is greater than the length of second guiding channel 41.Just, from suction chamber 142 via the distance of first guiding channel, 40 to first communication passage 32 greater than from the distance of suction chamber 142 via second guiding channel, 41 to second communication passage 33.
As shown in fig. 1, enabling by computer C of magnetic clutch 25 controlled.Computer C is connected to the switch W that is used to operate air regulator, the detection device F that is used for the setting device S of target setting room temperature and is used to detect room temperature.When switch W opened, control was used to enable and the electric current of inactive magnetic clutch 25 computer C according to the temperature difference between target room temperature and the room temperature that detected.
When the temperature that is detected was lower than target temperature, when perhaps working as the temperature that is detected and being higher than target temperature and the temperature difference and being within the allowed band, computer C closed towards the electric current of magnetic clutch 25.In this case, magnetic clutch 25 is in clutch (disengaged) state, and the driving force of vehicle motor 26 is not transferred to running shaft 21.When the temperature that is detected is higher than the temperature difference between target temperature and temperature that is detected and the target temperature and exceeds the permission level, computer C with electric current supply to magnetic clutch 25.In this case, magnetic clutch 25 is in jointing state, and the driving force of vehicle motor 26 is transferred to running shaft 21.
As shown in Fig. 2 B, first communication passage 32 has circular cross-section.As shown in Fig. 2 C, second communication passage 33 has circular cross-section.The diameter D of first communication passage 32 is set at the diameter d greater than second communication passage 33.Axle internal channel 31 has circular cross-section, and the diameter of axle internal channel 31 is set at the diameter D greater than first communication passage 32.
In Fig. 2 D, before representing, curve E discharges chamber 131 variation of temperature under the following conditions, promptly when remaining unchanged, the diameter d of second communication passage 33 changes the diameter D of first communication passage 32.Point on the curve E is represented actual measured value.Horizontal axis is represented the section ratio of the section area of the section area of first communication passage and second communication passage.This embodiment's section ratio (π D
2/ 4)/(π d
2/ 4) represent, wherein (π D
2/ 4) section area of expression first communication passage 32, and (π d
2/ 4) section area of expression second communication passage 33.Before representing, vertical axis discharges the temperature in the chamber 131.
Curve G in the plotted curve of Fig. 2 D is under the condition of the communication passage that has corresponding elongate section (for example, as in the reference No.6-129350 of technology as a setting as shown in).The size of respective elongated cross section on the axial direction of running shaft 21 is greater than the size on circumferential direction.Temperature when curve G represents along with the area change of elongate section in the discharge chamber 131 is with respect to the variation of section ratio.
In curve E and curve G, the total measurement (volume) of first pressing chamber 271 and second pressing chamber 281 is 200cc, and the rotating speed of double-headed piston type compressor 10 is 4500rpm, and head pressure Pd is 12 with the ratio of suction pressure Ps.
As shown in the plotted curve of Fig. 2 D, be lower than represented minimum temperature in section ratio is less than or equal to 1.8 scope by curve G by the temperature in the represented discharge chamber 131 of curve E.This is in the diameter D of first communication passage 32 diameter d greater than second communication passage 33, and what happens when being less than or equal to 1.8 times of diameter d in addition.Especially, be that 1.4 o'clock temperature becomes that to equal section ratio be 1 o'clock temperature at section ratio.That is, become and be lower than at diameter D if the diameter D of first communication passage 32, then discharges temperature in the chamber 131 greater than the diameter d of second communication passage 33 and when being less than or equal to 1.4 times of diameter d, d equates the temperature under the situation.When the diameter D of first communication passage 32 was 1.2 times of diameter d of second communication passage 33, the temperature of discharging in the chamber 131 was minimum.
According to preferred embodiment, can obtain following favourable effect.
(1) from suction chamber 142 via the distance of first guiding channel, 40 to first pressing chambers 271 greater than from the distance of suction chamber 142 via second guiding channel, 41 to second pressing chambers 281.In this case, suppose that the section area of communication passage 32,33 equates, then enter amount of coolant in first pressing chamber 271 and can be less than via second communication passage 33 and enter amount of coolant in second pressing chamber 281 via first communication passage 32.Therefore, the alterable compression ratio in first pressing chamber 271 must be higher than the compression ratio in second pressing chamber 281.Variable temperatures thus in the discharge chamber 131 must be higher than the temperature in the discharge chamber 141, back.
In this embodiment, the diameter D of first communication passage 32 is set at the diameter d greater than second communication passage 33, so that the section area of first communication passage 32 is set the section area greater than second communication passage 33 for.This structure can reduce via first communication passage 32 and enters the amount of coolant in first pressing chamber 271 and enter difference between the amount of coolant in second pressing chamber 281 via second communication passage 33.By reducing the difference of amount of coolant, the temperature that can suppress in first pressing chamber 271 freezing mixture by compression effectively raises.
(2) having first communication passage 32 of circular cross-section and second communication passage 33 is easy to make.
(3) when the diameter D of first communication passage 32 greater than the diameter d of second communication passage 33 and when being less than or equal to 1.8 times of diameter d, the temperature that can suppress in first pressing chamber 271 freezing mixture by compression effectively raises.
(4) when diameter D greater than diameter d and when being less than or equal to 1.4 times of diameter d, with diameter D, d equates to compare under the situation temperature that can suppress in first pressing chamber 271 freezing mixture by compression effectively and raises.
(5) when big 1.2 times of diameter D diameter group d, the temperature that can further suppress in first pressing chamber 271 freezing mixture by compression effectively raises.
(6) communication passage of routine techniques as a comparison has elongated cross section.Each elongate section size in the axial direction is set at greater than the size on circumferential direction.Suppose that the section area of the circulation passage of contrast equals the section area of circulation passage 32,33, then the diameter of circulation passage 32,33 is greater than the width (on the circumferential direction of rotary valve 35,36) of the elongate section of the circulation passage of contrast.Therefore, based on the rotation of rotary valve 35,36, open the time of the time of circulation passage 32,33 early than the circulation passage of opening elongate section.That notes is the time of " opening time " expression when outlet 312,313 beginnings of axle internal channel 31 are communicated with circulation passage 32,33.Similarly, based on the rotation of rotary valve 35,36, the time of closing circulation passage 32,33 is later than the time of the circulation passage of closing elongate section.What be also noted that is, " shut-in time " expression is when the state of the outlet 312,313 of axle internal channel 31 time when coupled condition changes to off state.Therefore, compare, utilize the structure of communication passage 32,33 can suitably improve the supply of the freezing mixture that enters pressing chamber 271,281 with circular cross-section with the communication passage of elongate section.
(7) the size Z1 that records in the axial direction owing to communication passage 32,33, Z2 (as shown in fig. 1) sets longlyer, so head 291,292 length X in the axial direction of double-head piston 29, Y (as shown in fig. 1) need set longlyer.When the length X of head 291,292, when Y set longlyer, the weight of double-head piston 29 can increase.
The diameter of the communication passage 32,33 of circular cross-section is less than the size on the axial direction of elongate section of the communication passage of contrast, and wherein Dui Bi communication passage has the section area equal with communication passage 32,33 respectively.Therefore, utilize the structure of communication passage 32,33 with circular cross-section, the length X of head 291,292, Y compares and can suitably shorten with the communication passage with elongate section.
(8) compare with the situation of the communication passage with elongate section, the circular cross-section of communication passage 32,33 can shorten communication passage 32,33 size Z1 in the axial direction, Z2.In suction process,, the end face of double-head piston 29 therefore becomes early than the situation of communication passage with elongate section when passing through 32,33 o'clock time of communication passage fully.Just, open 32,33 o'clock time set of communication passage fully when double-head piston 29 and must increase the supply of freezing mixture thus early than the situation of communication passage with elongate section.
The present invention is not limited to the foregoing description, but can be revised as following alternative embodiment.
Suction chamber can be formed in the front case 13, so that via axle internal channel 31 freezing mixture is introduced pressing chamber 271,281.
The suction pressure district can be arranged on the outside of compressor, so that freezing mixture is introduced first guiding channel and second guiding channel.First rotary valve 35 and second rotary valve 36 can be independent of running shaft 21 and form.
Therefore, this example and embodiment should be considered as descriptive and nonrestrictive, and the present invention is not limited to details given in the literary composition, but can make amendment within the scope of the appended claims.
Claims (4)
1. one kind is used for allowing freezing mixture to enter the suction structure of pressing chamber from the suction pressure district at double-headed piston type compressor, and described compressor comprises:
Cylinder body;
Running shaft by described cylinder body supporting;
The reciprocating double-head piston along with the rotation of described running shaft;
Be formed in the described cylinder body so that hold the first cylinder thorax and the second cylinder thorax of described double-head piston in paired mode;
First pressing chamber and second pressing chamber that in described first cylinder thorax and the described second cylinder thorax, limit respectively by described double-head piston;
Described suction structure in the described compressor comprises:
First rotary valve, it introduces described first pressing chamber with freezing mixture from described suction pressure district via first guiding channel;
Second rotary valve, it introduces described second pressing chamber with freezing mixture from described suction pressure district via second guiding channel, and wherein, the each several part of the each several part of described first guiding channel and described second guiding channel all is formed in the described running shaft;
First communication passage, it has circular cross-section and is formed in the described cylinder body, so that described first pressing chamber is connected on described first guiding channel; And
Second communication passage, it has circular cross-section and is formed in the described cylinder body, so that described second pressing chamber is connected on described second guiding channel, wherein, from described suction pressure district via described first guiding channel to the distance of described first communication passage greater than from described suction pressure district via the distance of described second guiding channel to described second communication passage, and wherein, the diameter of described first communication passage is greater than the diameter of described second communication passage, and
The diameter of described first communication passage is less than or equal to 1.8 times of diameter of described second communication passage.
2. suction structure according to claim 1 is characterized in that, the diameter of described first communication passage is less than or equal to 1.4 times of diameter of described second communication passage.
3. suction structure according to claim 1 is characterized in that, the part of shared described first guiding channel of described second guiding channel in the described running shaft.
4. double-headed piston type compressor comprises:
Cylinder body;
Running shaft by described cylinder body supporting;
The cam body that forms with described running shaft;
The double-head piston that engages with described cam body, wherein, the rotation of described running shaft is transferred to described piston via described cam body;
Be formed in the described cylinder body so that hold the first cylinder thorax and the second cylinder thorax of described double-head piston in paired mode;
First pressing chamber and second pressing chamber that in described first cylinder thorax and the described second cylinder thorax, limit respectively by described double-head piston;
With first rotary valve that described running shaft rotates with being integral, wherein, described first rotary valve has first guiding channel, so that freezing mixture is introduced described first pressing chamber from the suction pressure district via described first guiding channel;
Second rotary valve that rotates with described running shaft with being integral, wherein, described second rotary valve has second guiding channel, so that freezing mixture is introduced described second pressing chamber from described suction pressure district via described second guiding channel, wherein, the each several part of the each several part of described first guiding channel and described second guiding channel all is formed in the described running shaft;
First communication passage, it has circular cross-section and is formed in the described cylinder body, so that described first pressing chamber is connected on described first guiding channel; And
Second communication passage, it has circular cross-section and is formed in the described cylinder body, so that described second pressing chamber is connected on described second guiding channel, wherein, from described suction pressure district via described first guiding channel to the distance of described first communication passage greater than from described suction pressure district via the distance of described second guiding channel to described second communication passage, wherein, the diameter of described first communication passage is greater than the diameter of described second communication passage
Wherein, the diameter of described first communication passage is less than or equal to 1.8 times of diameter of described second communication passage.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2007267973 | 2007-10-15 | ||
| JP2007-267973 | 2007-10-15 | ||
| JP2007267973A JP2009097379A (en) | 2007-10-15 | 2007-10-15 | Refrigerant suction structure in double-headed piston type compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101413495A CN101413495A (en) | 2009-04-22 |
| CN101413495B true CN101413495B (en) | 2011-04-06 |
Family
ID=40534402
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2008101660535A Expired - Fee Related CN101413495B (en) | 2007-10-15 | 2008-10-13 | Suction structure in double-headed piston type compressor |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20090097999A1 (en) |
| JP (1) | JP2009097379A (en) |
| KR (1) | KR100988176B1 (en) |
| CN (1) | CN101413495B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5152007B2 (en) * | 2009-01-23 | 2013-02-27 | 株式会社豊田自動織機 | Lubrication structure in piston type compressor |
| CN101943153B (en) * | 2010-09-15 | 2012-07-04 | 奉化市华南汽车空调配件有限公司 | Split air condition compressor of automobile |
| JP6977651B2 (en) * | 2018-03-30 | 2021-12-08 | 株式会社豊田自動織機 | Piston compressor |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1432733A (en) * | 2001-11-21 | 2003-07-30 | 株式会社丰田自动织机 | Refrigerant sucker mechanism for piston-type compressor and the piston-type compressor |
| CN1904360A (en) * | 2005-07-27 | 2007-01-31 | 株式会社丰田自动织机 | Double-headed piston type compressor |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0613867B2 (en) * | 1985-12-25 | 1994-02-23 | 株式会社豊田自動織機製作所 | Swash plate type compressor |
| JPS63174579A (en) * | 1987-01-12 | 1988-07-19 | Canon Inc | Oscillatory wave motor |
| JPS63174579U (en) * | 1987-04-17 | 1988-11-11 | ||
| US4974702A (en) * | 1989-01-27 | 1990-12-04 | Kabushiki Kaisha Tyoda Jidoshokki Seisakusho | Swash plate type compressor with thrust bearing lubricator |
| JP3080278B2 (en) * | 1992-10-05 | 2000-08-21 | 株式会社豊田自動織機製作所 | Reciprocating compressor |
| US5380163A (en) * | 1993-02-23 | 1995-01-10 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Gas guiding mechanism in a piston type compressor |
| US5556260A (en) * | 1993-04-30 | 1996-09-17 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Multiple-cylinder piston type refrigerant compressor |
| JPH0821360A (en) * | 1994-07-04 | 1996-01-23 | Toyota Autom Loom Works Ltd | Reciprocating compressor of duplex piston type |
| JP2000145629A (en) * | 1998-11-11 | 2000-05-26 | Tgk Co Ltd | Variable displacement compressor |
| JP2003247486A (en) | 2001-12-21 | 2003-09-05 | Toyota Industries Corp | Lubrication structure of piston compressor |
| JP4003673B2 (en) * | 2003-03-13 | 2007-11-07 | 株式会社豊田自動織機 | Piston compressor |
| JP3855949B2 (en) * | 2003-03-18 | 2006-12-13 | 株式会社豊田自動織機 | Double-head piston compressor |
| JP3855952B2 (en) | 2003-03-24 | 2006-12-13 | 株式会社豊田自動織機 | Piston compressor |
| JP4730317B2 (en) * | 2007-02-02 | 2011-07-20 | 株式会社豊田自動織機 | Double-head piston compressor |
-
2007
- 2007-10-15 JP JP2007267973A patent/JP2009097379A/en active Pending
-
2008
- 2008-07-11 KR KR1020080067549A patent/KR100988176B1/en active IP Right Grant
- 2008-10-07 US US12/287,301 patent/US20090097999A1/en not_active Abandoned
- 2008-10-13 CN CN2008101660535A patent/CN101413495B/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1432733A (en) * | 2001-11-21 | 2003-07-30 | 株式会社丰田自动织机 | Refrigerant sucker mechanism for piston-type compressor and the piston-type compressor |
| CN1904360A (en) * | 2005-07-27 | 2007-01-31 | 株式会社丰田自动织机 | Double-headed piston type compressor |
Non-Patent Citations (2)
| Title |
|---|
| JP特开2007-2853A 2007.01.11 |
| JP特开2008-190386A 2008.08.21 |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101413495A (en) | 2009-04-22 |
| JP2009097379A (en) | 2009-05-07 |
| KR20090038352A (en) | 2009-04-20 |
| KR100988176B1 (en) | 2010-10-18 |
| US20090097999A1 (en) | 2009-04-16 |
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