CN100585176C - Double-ended piston compressor - Google Patents
Double-ended piston compressor Download PDFInfo
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- CN100585176C CN100585176C CN200680028005A CN200680028005A CN100585176C CN 100585176 C CN100585176 C CN 100585176C CN 200680028005 A CN200680028005 A CN 200680028005A CN 200680028005 A CN200680028005 A CN 200680028005A CN 100585176 C CN100585176 C CN 100585176C
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Abstract
Use is made of a structure of refrigerant suction into front compression space (28a) of double-ended piston refrigerant compressor that is different from that into rear compression space (29a). In particular, the structure of refrigerant suction into front compression space (28a) consists of suction valve (18a) of flap valve. On the other hand, the structure of refrigerant suction into rear compression space (29a) consists of rotary valve (35). Consequently, the pulsation of compressor can be dampened to thereby suppress any noise generation with the result that contribution to keeping of quietness can be attained.
Description
Technical field
The present invention relates to double-headed piston type compressor.
Background technique
Past is as the vehicle air conditioning compressor of vehicle, the double-headed piston type compressor that is for example using patent documentation 1 to be put down in writing.Be formed with a plurality of cylinder thoraxes that are used for holding double-head piston on the cylinder body of this compressor.The swash plate that moves with running shaft makes double-head piston to-and-fro motion in the cylinder thorax.The pressing chamber that has the both sides that are limited at double-head piston in each cylinder thorax of double-headed piston type compressor.Double-head piston is discharged outside pressing chamber the refrigeration agent after being inhaled into refrigeration agent in the pressing chamber and compressing and will compress.Patent documentation 1 is disclosed, is to adopt the rotary valve conduct that refrigeration agent is sucked the compressor of the refrigeration agent suction structure in each pressing chamber and adopts suction valve as the compressor that refrigeration agent is sucked the refrigeration agent suction structure in each pressing chamber.
Recently, become more quiet in order to make taking advantage of of vehicle (particularly automobile) drive indoor environment, motor develops to the solemn silence aspect.Meanwhile, people wish that also vehicle air conditioning also can become quiet with compressor.Yet as the existing compressor that patent documentation 1 is put down in writing, the pulsation (pressure surge) that is produced in the compressor can cause noise and vibration.This noise and vibration are delivered to take advantage of from compressor by pipe arrangement drives the indoor noise that produces.Therefore, with regard to existing compressor, recently require the solemn silenceization that reaches can't say the sufficient measure of having taked aspect horizontal satisfying people.
Patent documentation 1: Japanese kokai publication hei 5-312146 communique
Summary of the invention
The objective of the invention is, thereby provide a kind of pulsation that can alleviate compressor to suppress the generation of noise, help to realize the double-headed piston type compressor of solemn silenceization.
The invention provides a kind of have protecgulum, bonnet and be arranged on described protecgulum and described bonnet between the double-headed piston type compressor of cylinder body.Described cylinder body has a plurality of cylinder thoraxes.Described protecgulum, described bonnet and described cylinder body limit the swash plate chamber.Described compressor limits the suction pressure district.The double-head piston of intercalation slidably in described a plurality of cylinder thoraxes limits the pressing chamber of described protecgulum side and the pressing chamber of described bonnet side.One among described two pressing chambers is the 1st pressing chamber, and another is the 2nd pressing chamber.The swash plate that described compressor has running shaft rotatably supported in described cylinder body and rotates with described running shaft in described swash plate chamber.This swash plate makes the to-and-fro motion in described cylinder thorax of described double-head piston.Its result is drawn into described two pressing chambers from described suction pressure district refrigeration agent and compresses the back and discharge in this pressing chamber.Being used for described refrigeration agent is sucked the structure of described the 1st pressing chamber, is to have the rotary valve that described refrigeration agent is imported the importing path of described the 1st pressing chamber from described suction pressure district.Being used for described refrigeration agent is sucked the structure of described the 2nd pressing chamber, is the suction valve that opens and closes by the pressure reduction between described suction pressure district and described the 2nd pressing chamber.
Other features and advantages of the present invention can be understood by following detailed description and for feature of the present invention being described the drawing of enclosing.
Description of drawings
Fig. 1 is the sectional view of the double-headed piston type compressor of the 1st mode of execution that the present invention has been specialized.
Fig. 2 is the performance plot that the suction pulsation of compressor shown in Figure 1 and existing compressor is showed.
Fig. 3 is the amplification view that the major component of the double-headed piston type compressor of another example of the present invention is showed.
Fig. 4 is the sectional view of the double-headed piston type compressor of the present invention's the 2nd mode of execution.
Fig. 5 is the sectional view of the double-headed piston type compressor of the present invention's the 3rd mode of execution.
Fig. 6 is the sectional view of the double-headed piston type compressor of the present invention's the 4th mode of execution.
Fig. 7 is the sectional view of the double-headed piston type compressor of the present invention's the 5th mode of execution.
Embodiment
Below, the 1st mode of execution that the present invention specialized is described in conjunction with Fig. 1, Fig. 2.Fig. 1 is the sectional view of the double-headed piston type compressor (being designated hereinafter simply as " compressor ") 10 of the 1st mode of execution.In addition, in Fig. 1 and Fig. 4～Fig. 7, the left side is the front side of compressor 10, and the right side is the rear side of compressor 10.
As shown in Figure 1, the whole casing of compressor 10 comprise front side (left side of Fig. 1) front-bank rotor housing 11, be bonded on the rear-bank rotor housing 12 of protecgulum 13 on this front-bank rotor housing 11, rear side (right side of Fig. 1) and be bonded on bonnet 14 on this rear-bank rotor housing 12. Cylinder body 11,12 is bonded with each other together. Cylinder body 11,12, protecgulum 13 and bonnet 14 are tightened to one by many (for example 5) bolt B.Fig. 1 only illustrates a bolt hole BH and the bolts B in this bolt hole BH.Each bolt B is on cylinder body 11,12, protecgulum 13 and the bonnet 14 among formed a plurality of (for example 5) bolt hole BH.Formed screw section N screw thread is combined on the bonnet 14 on the end of bolt B.The diameter of each bolt hole BH is greater than the diameter of bolt B.When bolt B runs through each spiral shell inspection through hole BH, limit blank part S in each bolt hole BH.
Be formed with the inlet hole P of perforation on the outer circumferential face of front-bank rotor housing 11 to the inner peripheral surface of this front-bank rotor housing 11.The external refrigerant loop that is laid in the outside of compressor 10 is connected on the inlet hole P.Be formed with the not shown tap hole of perforation on the outer circumferential face of front-bank rotor housing 11 to the inner peripheral surface of this front-bank rotor housing 11.Described external refrigerant loop is connected on this tap hole.
When using refrigerant circulation loop with compressor 10 formation vehicle air conditionings, described external refrigerant loop is connected to the head pressure district of compressor 10 in the suction pressure district.Described external refrigerant loop has condenser, expansion valve and vaporizer.Condenser, expansion valve and vaporizer externally on the refrigerant circuit head pressure district from compressor 10 set gradually.
Be provided with valve plate 19 between bonnet 14 and the rear-bank rotor housing 12, discharge trap 20 and limiter formation plate 21.Be formed with exhaust port 19a at valve plate 19 with discharging on the corresponding position of chamber 14a.In addition, discharge trap 20 with the corresponding position of exhaust port 19a on be formed with back expulsion valve 20a.Back expulsion valve 20a as clack valve is used for opening and closing exhaust port 19a.The valve of discharging formed back expulsion valve 20a on the trap 20 is sized to size X.The valve size here is meant the size of the butt of the back expulsion valve 20a that is pushed by the partition wall that limits discharge chamber 14a in bonnet 14 to the end of back expulsion valve 20a.In the present embodiment, the valve size (size X) of preceding expulsion valve 16a and the valve size (size X) of back expulsion valve 20a are set at same valve size.That is, the structure of discharging trap 16,20 is identical, is formed with valve measure-alike expulsion valve 16a, 20a on this discharge trap 16,20 respectively.In addition, limiter forms and to be formed with the limiter 21a that the aperture to back expulsion valve 20a limits on the plate 21.
Running shaft 22 is rotatably supported in cylinder body 11,12.Running shaft 22 interts among axis hole 11a, the 12a that forms running through cylinder body 11,12.The state that runs through the through hole 15c of running shaft 22 with the central authorities of valve plate 15 before being formed at interts.In addition, the inner peripheral surface of the outer circumferential face of running shaft 22 and through hole 15c has constituted the slide part of running shaft 22.Running shaft 22 directly obtains the supporting of cylinder body 11,12 by axis hole 11a, 12a.Be provided with lip seal profile shaft seal apparatus 23 between protecgulum 13 and the running shaft 22.Gland seal device 23 is accommodated on the protecgulum 13 in the formed sealing accommodation chamber 13c.Before discharge chamber 13a and preceding suction chamber 13b be arranged on sealing accommodation chamber 13c around.
Fixing the swash plate 24 that rotates with this running shaft 22 on the running shaft 22.Swash plate 24 is arranged in the swash plate chamber 25 that is limited between the cylinder body 11,12.Be provided with thrust-bearing 26 between the base portion 24a of the ring of the end face of front-bank rotor housing 11 and swash plate 24.Be provided with thrust-bearing 27 between the base portion 24a of the end face of rear-bank rotor housing 12 and swash plate 24.Thrust-bearing 26,27 is clipped in the middle swash plate 24, to its mobile restriction on the centre line L direction of running shaft 22.
Be formed with on the front-bank rotor housing 11 and be arranged in running shaft 22 a plurality of preceding cylinder thorax 28 (be 5 in the present embodiment, a preceding cylinder thorax 28 only is shown among Fig. 1) on every side.In addition, be formed with on the rear-bank rotor housing 12 be arranged in running shaft 22 around a plurality of back cylinder thoraxes 29 (be 5 in the present embodiment, only illustrate among Fig. 1 after cylinder thorax 29).In the paired cylinder thorax 28,29 in front and back, accommodate double-head piston 30 as the double head type piston.Cylinder body 11,12 has constituted the pressure cylinder of double-head piston 30 usefulness.In addition, be formed with the communication paths R2 that swash plate chamber 25 is communicated with back suction chamber 14b on rear-bank rotor housing 12 and the bonnet 14.
Swash plate 24 moves with running shaft 22, thereby is integral rotation with running shaft 22.This rotatablely moving of swash plate 24 is delivered on the double-head piston 30 by a pair of piston shoes 31 that swash plate 24 is clipped in the middle.Its result, double-head piston 30 carries out the to-and-fro motion of fore-and-aft direction in cylinder thorax 28,29.In cylinder thorax 28,29, limit as the preceding pressing chamber 28a of the 1st pressing chamber with as the back pressing chamber 29a of the 2nd pressing chamber by double-head piston 30.On the inner peripheral surface of wherein axis hole 11a, 12a, be formed with sealing side face 11b, 12b at running shaft 22.Running shaft 22 directly obtains the supporting of cylinder body 11,12 by sealing side face 11b, 12b.In the present embodiment, inlet hole P and bolt hole BH are opened on the swash plate chamber 25 of compressor 10.
Be formed with in the running shaft 22 as the supply passage 22a that imports path.Supply passage 22a is by carry out the poroid path that perforate processing forms on the end face as bonnet 14 sides of the running shaft 22 of solid shaft.Therefore, the back suction chamber 14b of the end opening of supply passage 22a in bonnet 14.In addition, running shaft 22 with rear-bank rotor housing 12 corresponding positions on, be formed with the communication paths 32 that is communicated with supply passage 22a.The running shaft 22 outer circumferential face side openings of communication paths 32 play a role as the outlet 32b of communication paths 32.In addition, be formed with a plurality of suction paths 33 (be 5 in the present embodiment, a suction path 33 only is shown among Fig. 1) that back cylinder thorax 29 is communicated with axis hole 12a on the rear-bank rotor housing 12.Suck that path 33 has the inlet 33a that is opened on the sealing side face 12b and towards the outlet 33b of back pressing chamber 29a opening.Along with the rotation of running shaft 22, the outlet 32b of communication paths 32 intermittently realizes being communicated with the inlet 33a that each sucks path 33.The part that the sealed side face 12b of running shaft 22 surrounds is as playing a role with the integrally formed rotary valve 35 of running shaft 22.
In the compressor 10 of present embodiment, the refrigeration agent suction structure of pressing chamber 29a is different after refrigeration agent (gas) being sucked the suction structure of preceding pressing chamber 28a and refrigeration agent being sucked.Specifically, the refrigeration agent suction structure of preceding pressing chamber 28a has the clack valve 18a that is arranged between preceding suction chamber 13b and the preceding pressing chamber 28a.Pressure reduction between forward suction chamber 13b of clack valve 18a and the preceding pressing chamber 28a opens and closes.The refrigeration agent suction structure of back pressing chamber 29a has the rotary valve 35 that is arranged between back suction chamber 14b and the back pressing chamber 29a.Rotary valve 35 has the supply passage 22a that the refrigeration agent of preceding suction chamber 13b (gas) is imported back pressing chamber 29a.
The pressing chamber that will lean on rotary valve 35 suction refrigeration agents will lean on clack valve 18a to suck the pressing chamber of refrigeration agent as the 2nd pressing chamber as the 1st pressing chamber.In the present embodiment, preceding pressing chamber 28a is the 2nd pressing chamber, and back pressing chamber 29a is the 1st pressing chamber.In the compressor 10 that as above constitutes, when preceding cylinder thorax 28 is in suction stroke, when promptly double-head piston 30 is from the stroke that moves to the right in the left side of Fig. 1, pressing chamber 28a before the refrigeration agent of preceding suction chamber 13b will be inhaled into via clack valve 18a.That is to say that shown in the arrow of Fig. 1, the refrigeration agent in external refrigerant loop is inhaled in the swash plate chamber 25 by inlet hole P, afterwards, flow through bolt hole BH and communication paths R1 arrive among the preceding suction chamber 13b of protecgulum 13.Refrigeration agent in the preceding suction chamber 13b that plays a role as the suction pressure district is by the pressure reduction that is produced between suction chamber 13b before being somebody's turn to do and the preceding pressing chamber 28a (preceding cylinder thorax 28) clack valve 18a the past suction port 15b to be backed down and be inhaled into preceding pressing chamber 28a's.
And when preceding cylinder thorax 28 is in the discharge stroke, when being double-head piston 30 from the stroke that moves to the left on the right side of Fig. 1, the refrigeration agent in the preceding pressing chamber 28a with preceding expulsion valve 16a in the past exhaust port 15a back down and discharge to the preceding discharge chamber 13a that plays a role as the head pressure district.The not shown communication paths of flowing through refrigeration agent before being discharged in the discharge chamber 13a flows out to outside refrigerant circuit from tap hole.Put into lubricant oil in the refrigerant circulation loop that is made of compressor 10 and external refrigerant loop, this lubricant oil flows with refrigeration agent.
In addition, when back cylinder thorax 29 is in suction stroke, when promptly double-head piston 30 is from the stroke that moves to the left on the right side of Fig. 1, the outlet 32b of communication paths 32 will be communicated with the inlet 33a that sucks path 33.Therefore, the refrigeration agent of back suction chamber 14b is inhaled among the pressing chamber 29a of back via rotary valve 35.That is to say that shown in the arrow of Fig. 1, the refrigeration agent in external refrigerant loop is inhaled in the swash plate chamber 25 by inlet hole P, afterwards, the communication paths of flowing through R2 arrives back suction chamber 14b.The refrigeration agent of the back suction chamber 14b that plays a role as the suction pressure district is by the effect of rotary valve 35, and the supply passage 22a that flows through, communication paths 32 and suction path 33 are inhaled in the back pressing chamber 29a of back cylinder thorax 29.
And when back cylinder thorax 29 is in the discharge stroke; When being double-head piston 30 from the stroke that moves to the right in the left side of Fig. 1, the refrigeration agent in the back pressing chamber 29a backs down back expulsion valve 20a from exhaust port 19a, to the back discharge chamber 14a discharge that plays a role as the head pressure district.The not shown communication paths of flowing through refrigeration agent after being discharged in the discharge chamber 14a flows out to outside refrigerant circuit from tap hole.
Below, the working principle of the compressor 10 of present embodiment is described in conjunction with Fig. 2.
Fig. 2 shows the measurement result of suction pulsation in two kinds of related experimental setups of the refrigerant circulation loop that comprises double-headed piston type compressor and outside link circuit, described compressor.That is, Fig. 2 shows the measurement result of suction pulsation of the compressor among have dotted line this case device A1 of characteristic of " A1 " and the measurement result with suction pulsation of the compressor among the existing apparatus A2 of characteristic of solid line " A2 ".Compressor among this case device A1 comprises refrigeration agent suction structure that is made of clack valve and the refrigeration agent suction structure that is made of rotary valve as the compressor 10 of the 1st mode of execution.Compressor among the existing apparatus A2 then as above-mentioned existing compressor, possesses the refrigeration agent suction structure that is made of clack valve in both sides.With regard to this case device A1 and existing apparatus A2, the refrigeration agent suction structure that is described compressor there are differences, and the structure in other structure example such as external refrigerant loop is all set according to the same terms.
Fig. 2 illustrates the rotational speed N C suction pulsation when low engine speed range 500～2000rpm, particular frequency range of compressor.In the present embodiment, speed range is set at suction valve generation self-excited vibration and sound that this vibration produced becomes a kind of like this rotational speed N C scope of noise for the occupant.When the clack valve generation self-excited vibration that plays a role as suction valve, thereby this vibration will be delivered to the sound that generation is trembleed this pipe arrangement and vaporizer on the vaporizer by pipe arrangement.In addition, specific frequency range is 400～1000Hz, and this value is to set according to the resonant frequency scope of employed vaporizer in the external refrigerant loop.
By the measurement result of Fig. 2 as can be known, in the whole frequency range of 400～1000Hz, the suction of this case device A1 pulsation is all lighter than the suction pulsation of existing apparatus A2.That is,,, compressor 10 overall suction pulsation realized solemnly silentization owing to alleviating for the refrigerant circulation loop that uses this case device A1.In addition, according to this case device A1, " 700Hz " that reach peak value in the suction of existing apparatus A2 pulsation locates, and it sucks the reduced rate maximum of pulsation.Specifically, with regard to the reduced rate of the suction pulsation of locating at " 700Hz " with regard to this case device A1, if the peak value of the suction pulsation of existing apparatus A2 is set at " 100% ", then its reduced rate has reached about " 90% ".In addition, for existing apparatus A2, the reduced rate of the suction of this case device A1 pulsation has surpassed 50% mostly in the frequency range of 400～1000Hz.
In the compressor 10 of present embodiment, the refrigeration agent suction structure of preceding pressing chamber 28a is clack valve 18a, and the refrigeration agent suction structure of back pressing chamber 29a is a rotary valve 35.Clack valve 18a structurally different with rotary valve 35 thereby when sucking refrigeration agent their process (action) differ from one another.That is, clack valve 18a is that a kind of pressured difference is implemented the structure that opens and closes, thereby before refrigeration agent sucked during pressing chamber 28a, the opening and closing of clack valve 18a will produce hysteresis.And rotary valve 35 is arranged on the running shaft 22 and with running shaft 22 actions.Therefore, when refrigeration agent is sucked back pressing chamber 29a, be with being communicated with of back pressing chamber 29a refrigeration agent to be forced to suck this back pressing chamber 29a's by supply passage 22a (communication paths 32).Because there is above-mentioned difference in process, thereby will produce phase difference between suction opportunity of the suction opportunity of preceding pressing chamber 28a and back pressing chamber 29a.Therefore, the intake of preceding pressing chamber 28a will be less than the intake of back pressing chamber 29a.
That is to say the refrigerant density of the back pressing chamber 29a after the refrigerant density of the preceding pressing chamber 28a after suction stroke finishes finishes less than suction stroke.Therefore, transferring to from suction stroke when discharging stroke, producing phase difference between discharge opportunity of the discharge opportunity of preceding pressing chamber 28a and back pressing chamber 29a.That is, preceding pressing chamber 28a discharges opportunity that chamber 13a discharges and back pressing chamber 29a forward and discharges backward between opportunity of chamber 14a discharge and produce phase difference.Before pressing chamber 28a to discharge the opportunity that chamber 13a discharges forward slower than the opportunity that back pressing chamber 29a discharges chamber 14a discharge backward.Its result, for the compressor 10 of present embodiment, it is very high that the peak value of the pulsating waveform of specific times can not reach, and peak value reduces.That is, the discharge of compressor 10 pulsation reduces.
Below, before for example considering the refrigeration agent suction structure of the refrigeration agent suction structure of pressing chamber 28a and back pressing chamber 29a the two be clack valve or the two is rotary valve and has a kind of like this situation of same structure.In this case, the refrigeration agent suction structure of preceding pressing chamber 28a presents identical process (action) with the refrigeration agent suction structure of back pressing chamber 29a when sucking refrigeration agent.Therefore, there is not phase difference between suction opportunity of the suction opportunity of preceding pressing chamber 28a and back pressing chamber 29a.Therefore, do not have difference between the refrigerant density of the refrigerant density of preceding pressing chamber 28a and back pressing chamber 29a, thereby can not produce difference between discharge opportunity of the discharge opportunity of preceding pressing chamber 28a and back pressing chamber 29a.Like like this, if the refrigeration agent suction structure of preceding pressing chamber 28a is identical with the refrigeration agent suction structure of back pressing chamber 29a, then the discharge of specific times pulsation is concentrated and is occurred, and the peak value of pulsating waveform increases, and can bring noise and vibration to cause the problem of noise.
Therefore, present embodiment has the following advantages.
(1) the refrigeration agent suction structure of preceding pressing chamber 28a is different from the refrigeration agent suction structure of back pressing chamber 29a.In the present embodiment, the refrigeration agent suction structure of preceding pressing chamber 28a side is clack valve 18a, and the refrigeration agent suction structure of back pressing chamber 29a side is a rotary valve 35.Therefore, can alleviate the suction pulsation that produces in the compressor 10.Therefore, thereby can alleviate the generation that pulsation in the compressor 10 suppresses noise, help to realize solemn silenceization.
(2) the inlet hole P that is connected on the external refrigerant loop is arranged on the front-bank rotor housing 11.That is, for preceding pressing chamber 28a and back pressing chamber 29a, via swash plate chamber 25 supply system cryogens.Therefore, refrigeration agent is that pressing chamber 28a and back pressing chamber 29a disperse to supply with before the mediad of compressor 10, can suppress the reduction of suction efficiency.That is to say, the suction efficiency of a certain side's pressing chamber 28a, 29a is reduced.
(3) the supply passage 22a of rotary valve 35 is the poroid paths that are opened on the end of running shaft 22.Therefore, the opening end that can pass through running shaft 22 improves the refrigeration agent suction efficiency to rotary valve 35 supply system cryogens.That is,, on constant position, rotate all the time, thereby the supply of refrigeration agent is very easy to because supply passage 22a is communicated with back suction chamber 14b all the time.
(4) rotary valve 35 that will have a poroid path has been located at bonnet 14 sides.If such as poroid path is set in running shaft 22, rotary valve is set in protecgulum 13 sides, then must in running shaft 22, poroid path be set with the state that extends to protecgulum 13 sides from bonnet 14 sides.This will cause the intensity of running shaft 22 to reduce.With respect to this, if as present embodiment, be the rotary valve 35 of poroid path form, so as long as poroid path is set in the part of bonnet 14 sides of running shaft 22 in bonnet 14 side settings.Therefore, present embodiment can suppress the intensity reduction of running shaft 22.That is, present embodiment is favourable aspect intensity that guarantees running shaft 22 and ease of processing.
(5) rotary valve 35 is located at bonnet 14 sides.With for example, rotary valve be arranged on because of rich inadequately protecgulum 13 sides in gland seal device 23 spaces are set compare, present embodiment is easier to guarantee to suck with respect to the refrigeration agent of rotary valve the formation of path.In the present embodiment, supply passage 22a plays a role as the suction path that carries out the refrigeration agent suction with respect to rotary valve 35.
In addition, rotary valve 35 is arranged on bonnet 14 sides, compares with rotary valve being arranged on reverse, also help overcoming the problem that this type load brings with bigger protecgulum 13 sides of loads such as bending.That is to say, rotary valve 35 is arranged on protecgulum 13 sides, compare, influenced by above-mentioned load and cause the possibility that slight deformation take place rotary valve 35 and cylinder body 11,12 to increase with rotary valve 35 being arranged on bonnet 14 sides.This distortion can make between rotary valve 35 and the cylinder body 11,12 and produce the gap.Have, this distortion might cause refrigeration agent to leak between a plurality of suction paths 33 that cylinder thorax 28,29 is communicated with axis hole 11a, 12a again.Its result might reduce the suction efficiency of rotary valve 35, causes the efficient of compressor to reduce.Therefore, the present embodiment that rotary valve 35 is set in bonnet 14 sides can avoid rotary valve 35 and rear-bank rotor housing 12 to deform.Its result can avoid the suction efficiency of rotary valve 35 to reduce, and then avoids the efficient of compressor to reduce.
(6) in addition, rotary valve 35 is arranged on bonnet 14 sides, is formed with the back suction chamber 14b that is communicated with all the time with rotary valve 35 on the bonnet 14.Therefore, refrigeration agent temporarily can be remained among the suction chamber 14b of back.That is to say, formed and make refrigeration agent easily be inhaled into the structure of rotary valve 35.
(7) must be measure-alike with the valve size design of preceding expulsion valve 16a with the valve of back expulsion valve 20a.Therefore, can make that the exhaust structure of compressor 10 both sides is identical, can suppress the raising of manufacture cost.
Below, the 2nd mode of execution of the present invention is described in conjunction with Fig. 4.In following each mode of execution that describes, all structures identical with the mode of execution that has illustrated are all given identical reference character and duplicate explanation are omitted or simplification.
As shown in Figure 4, in the present embodiment, the valve size b that discharges the back expulsion valve 20a on the trap 20 designs than the big (a＜b) of the valve size a that discharges the preceding expulsion valve 16a on the trap 16.That is, the valve size of the preceding expulsion valve 16a at 13a place, preceding discharge chamber is different with the valve size of the back expulsion valve 20a at back discharge 14a place, chamber.Because the valve size of preceding expulsion valve 16a is different with the valve size of back expulsion valve 20a, thereby the rigidity of preceding expulsion valve 16a is different with the rigidity of back expulsion valve 20a.Process when therefore, preceding expulsion valve 16a opens and closes with back expulsion valve 20a is also different.Therefore, preceding pressing chamber 28a discharges opportunity that chamber 13a discharges and back pressing chamber 29a forward and discharges backward between opportunity of chamber 14a discharge and produce phase difference.Therefore, with the refrigeration agent suction structure that constitutes by clack valve 18a and alleviate effect by the pulsation that the refrigeration agent suction structure that rotary valve 35 constitutes is produced and complement each other, the peak value of the pulsation of specific times is further reduced.
Present embodiment also has the following advantages except aforementioned advantages (1)～(6) with the 1st mode of execution.
(8) it is different with the valve size of the back expulsion valve 20a of the refrigeration agent discharge that is used for sucking via rotary valve 35 to be used for the valve size of the preceding expulsion valve 16a that will discharge via the refrigeration agent that clack valve 18a sucks.Therefore, when the past pressing chamber 28a and back pressing chamber 29a discharging refrigerant, each expulsion valve 16a, 20a present different processes, and discharge produces phase difference opportunity.Therefore, can further alleviate the discharge pulsation of compressor 10.
Below, the 3rd mode of execution of the present invention is described in conjunction with Fig. 5.
Same with the compressor 10 in the 1st, the 2nd mode of execution, in the compressor 10 of present embodiment, the refrigeration agent suction structure of preceding pressing chamber 28a is clack valve 18a, and the refrigeration agent suction structure of back pressing chamber 29a is a rotary valve 35.As present embodiment, be used for that access structure and the 1st, the 2nd mode of execution supplied with of pressing chamber 29a is different backward via rotary valve 35 with refrigeration agent.To attach most importance to the access structure of present embodiment below and describe.
Be formed with on the running shaft 22 as the supply passage 22b that imports path.The supply passage 22b of present embodiment comprises poroid passage portion 36 and the groove shape passage portion 37 that links to each other with this poroid passage portion 36.Poroid passage portion 36 is to implement perforate processing as the end face of the running shaft 22 of solid shaft and forming.Groove shape passage portion 37 is to implement fluting to process and form on the outer circumferential face of running shaft 22.In addition, communication paths R3 on rear-bank rotor housing 12 according to swash plate chamber 25 is formed with the mode that axis hole 12a is communicated with.Groove shape passage portion 37 is according to the suction path 33 on the rear-bank rotor housing 12 is formed with the mode that communication paths R3 is communicated with.
In the compressor 10 that as above constitutes, when back cylinder thorax 29 was in suction stroke, when promptly double-head piston 30 was from the stroke that moves to the left on the right side of Fig. 5, the groove shape passage portion 37 of supply passage 22b was communicated with the inlet 33a of suction path 33.The refrigeration agent of the swash plate chamber 25 that plays a role as the suction pressure district is inhaled among the pressing chamber 29a of back via rotary valve 35.That is to say that shown in the arrow of Fig. 5, the refrigeration agent in external refrigerant loop is inhaled into swash plate chamber 25 by inlet hole P, afterwards, the communication paths of flowing through R3 arrives the groove shape passage portion 37 of supply passage 22b.Afterwards, the refrigeration agent of supply passage 22b is put among the 29a via sucking to compress after path 33 is inhaled into by the effect of rotary valve 35.
And when back cylinder thorax 29 is in the discharge stroke, when being double-head piston 30 from the stroke that moves to the right in the left side of Fig. 5, the refrigeration agent of back pressing chamber 29a backs down back expulsion valve 20a from exhaust port 19a, discharge to the back discharge chamber 14a that plays a role as the head pressure district.The not shown communication paths of flowing through refrigeration agent after being discharged among the discharge chamber 14a flows out to outside refrigerant circuit from tap hole.When preceding cylinder thorax 28 is in suction stroke and when discharging stroke, flowing of refrigeration agent is identical with the 1st, the 2nd mode of execution.The compressor 10 of present embodiment has refrigeration agent suction structure that is made of clack valve 18a and the refrigeration agent suction structure that is made of rotary valve 35, thereby has the effect same with the compressor 10 of the 1st, the 2nd mode of execution.
Therefore, present embodiment except have with the same advantage of the advantage (8) of advantage (1), (2), (5), (6) and the 2nd mode of execution of the 1st mode of execution, also have the following advantages.
(9) the supply passage 22b of rotary valve 35 is combined by poroid passage portion 36 and groove shape passage portion 37.Therefore, can increase the volume that is inhaled into the refrigeration agent in the rotary valve 35.
Below, the 4th mode of execution of the present invention is described in conjunction with Fig. 6.
In the compressor 10 of present embodiment, the refrigeration agent suction structure of preceding pressing chamber 28a is a rotary valve 49, and the refrigeration agent suction structure of back pressing chamber 29a is clack valve 46a.That is, two refrigeration agent suction structures in the compressor 10 of present embodiment are opposite with the 1st～the 3rd mode of execution.
In other words, the pressing chamber that will lean on rotary valve 49 suction refrigeration agents will lean on clack valve 46a to suck the pressing chamber of refrigeration agent as the 2nd pressing chamber as the 1st pressing chamber.In the present embodiment, preceding pressing chamber 28a is the 1st pressing chamber, and back pressing chamber 29a is the 2nd pressing chamber.
In the present embodiment, only be formed with the preceding chamber 13a of discharge on the protecgulum 13 and removed preceding suction chamber 13b.Be formed with the back on the bonnet 14 and discharge chamber 14a and back suction chamber 14b.Be provided with valve plate 40 between protecgulum 13 and the front-bank rotor housing 11, discharge trap 41 and limiter formation plate 42.Valve plate 40 with the corresponding position of preceding discharge chamber 13a on be formed with before exhaust port 40a.In addition, discharge trap 41 with the corresponding position of preceding exhaust port 40a on be formed with before expulsion valve 41a.Limiter forms and to be formed with the limiter 42a that the aperture to preceding expulsion valve 41a limits on the plate 42.
On the other hand, be provided with valve plate 43, discharge trap 44, limiter formation plate 45 and suction trap 46 between bonnet 14 and the rear-bank rotor housing 12.Valve plate 43 have be formed at discharge the corresponding locational back exhaust port 43a of chamber 14a with the back and be formed at back suction chamber 14b corresponding locational after suction port 43b.In addition, discharging trap 44 has and is formed at the corresponding locational back expulsion valve 44a with back exhaust port 43a.In the present embodiment, the valve size c of preceding expulsion valve 41a sets than the big (c＞d) of the valve size d of back expulsion valve 44a.Limiter forms and to be formed with the limiter 45a that the aperture to back expulsion valve 44a limits on the plate 45.Sucking trap 46 has and is formed at the corresponding locational clack valve 46a with back suction port 43b.Clack valve 46a is used for opening and closing back suction port 43b.Rear-bank rotor housing 12 has the breach 12c that forms accordingly with clack valve 46a.The wall of this breach 12c plays a role as the back suction limiter that the aperture to clack valve 46a limits.
Be formed with on the running shaft 22 as the supply passage 47 that imports path.The supply passage 47 of present embodiment is to implement fluting processing on as the outer circumferential face of the running shaft 22 of solid shaft and the groove shape path that forms.One end opening of supply passage 47 is in the sealing accommodation chamber 13c that holds gland seal device 23.In addition, be formed with a plurality of suction paths 48 (be 5 in the present embodiment, a suction path 48 only is shown among Fig. 6) that form according to the mode that preceding cylinder thorax 28 is communicated with axis hole 11a on the front-bank rotor housing 11.The inlet 48a that sucks path 48 sealing side face 11b upper shed in supply passage 47 corresponding positions on.Along with the rotation of running shaft 22, the inlet 48a that sucks path 48 intermittently realizes being communicated with supply passage 47.The part that the sealed side face 11b of running shaft 22 surrounds plays a role as integrally formed rotary valve 49 on running shaft 22.
In addition, be formed with the communication paths 50 that connects them on protecgulum 13 and the front-bank rotor housing 11.Communication paths 50 is positioned at the downside of front-bank rotor housing 11, passes through from the slit between adjacent two cylinder thoraxes 28,29.The inlet 50a of communication paths 50 is opened on swash plate chamber 25, and the outlet 50b of communication paths 50 is opened on sealing accommodation chamber 13c.That is, communication paths 50 is connected with sealing accommodation chamber 13c and swash plate chamber 25.In addition, be formed with the communication paths R4 that back suction chamber 14b is communicated with bolt hole BH on the bonnet 14.
In the compressor 10 that as above constitutes, when preceding cylinder thorax 28 is in suction stroke, when being double-head piston 30 from the stroke that moves to the right in the left side of Fig. 6, supply passage 47 is communicated with the inlet 48a that sucks path 48, and refrigeration agent is inhaled among the preceding pressing chamber 28a via rotary valve 49.That is to say that shown in the arrow of Fig. 6, the refrigeration agent in external refrigerant loop is inhaled in the swash plate chamber 25 by inlet hole P, the communication paths of flowing through afterwards 50 arrives sealing accommodation chamber 13c.And the effect of the refrigeration agent in the sealing accommodation chamber 13c that plays a role as the suction pressure district by rotary valve 49 via supply passage 47 and suck path 48 be inhaled into before among the pressing chamber 28a.
And be in when discharging stroke at preceding cylinder thorax 28, promptly double-head piston 30 is from the right side of Fig. 6 when mobile to the left, the refrigeration agent in the preceding pressing chamber 28a with preceding expulsion valve 41a in the past exhaust port 40a back down, be discharged to the preceding discharge chamber 13a that plays a role as the head pressure district.Flow out to outside refrigerant circuit from tap hole and discharge refrigeration agent among the 13a of the chamber not shown communication paths of flowing through before being discharged to.
On the other hand, when back cylinder thorax 29 was in suction stroke, promptly double-head piston 30 was from the right side of Fig. 6 when mobile to the left, and the refrigeration agent of back suction chamber 14b is inhaled into afterwards among the pressing chamber 29a via clack valve 46a.That is to say that shown in the arrow of Fig. 6, the refrigeration agent in external refrigerant loop is inhaled in the swash plate chamber 25 by inlet hole P, flow through afterwards bolt hole BH and communication paths R4 arrive the back suction chamber 14b of bonnet 14.And the refrigeration agent in the back suction chamber 14b that plays a role as the suction pressure district by the pressure reduction of generation between this back suction chamber 14b and the back pressing chamber 29a (back cylinder thorax 29) with clack valve 46a from after suction port 43b back down, thereby after being inhaled among the pressing chamber 29a.
And be in when discharging stroke at back cylinder thorax 29, promptly from the left side when mobile to the right, the refrigeration agent in the back pressing chamber 29a backs down expulsion valve 44a double-head piston 30 from back exhaust port 43a in Fig. 6, is discharged to the back discharge chamber 14a that plays a role as the head pressure district.The not shown communication paths of flowing through refrigeration agent after being discharged in the discharge chamber 14a flows out to outside refrigerant circuit from tap hole.
Two refrigeration agent suction structures of the compressor 10 of present embodiment comprise clack valve 46a and rotary valve 49.Therefore, present embodiment also can access the effect same with the compressor 10 of the 1st～the 3rd mode of execution.That is, though the setting and the 1st of clack valve 46a in the compressor 10 of present embodiment and rotary valve 49～the 3rd mode of execution is opposite, the effect that can reach be identical.
Therefore, according to present embodiment, except have with the same advantage of the advantage (8) of advantage (1), (2) and the 2nd mode of execution of the 1st mode of execution, also have the following advantages.
(10) supply passage 47 of rotary valve 49 is a groove shape path.Therefore, compare to form poroid path, the manufacture cost of running shaft 22 is reduced with on running shaft 22, implementing perforate processing.
(11) supply with to rotary valve 49 from the refrigeration agent of swash plate chamber 25 sealing accommodation chamber 13c via gland seal device 23.Therefore, can cool off gland seal device 23 with refrigeration agent.Thereby can improve the life-span of gland seal device 23, and can prevent that the characteristic of the lubricant oil of gland seal device 23 from changing.
Below, the 5th mode of execution of the present invention is described in conjunction with Fig. 7.
Same with compressor 10 illustrated in the 4th mode of execution, the refrigeration agent suction structure of the preceding pressing chamber 28a in the compressor 10 of present embodiment is a rotary valve 49, and the refrigeration agent suction structure of back pressing chamber 29a is clack valve 46a.In the present embodiment, be used for that the access structure of pressing chamber 28a supply system cryogen is different with the 4th mode of execution forward via rotary valve 49.
As shown in Figure 7, be formed with supply passage 51 on the running shaft 22.The supply passage 51 of present embodiment is to implement fluting processing on as the outer circumferential face of the running shaft 22 of solid shaft and the groove shape path that forms.Communication paths R5 on front-bank rotor housing 11 according to swash plate chamber 25 is formed with the mode that axis hole 11a is communicated with.Supply passage 51 forms according to the mode that a plurality of suction paths 48 (be 5 in the present embodiment, a suction path 48 only is shown among Fig. 7) that make on the front-bank rotor housing 11 are communicated with communication paths R5.
In the compressor 10 that as above constitutes, when preceding cylinder thorax 28 is in suction stroke, when being double-head piston 30 from the stroke that moves to the right in the left side of Fig. 7, supply passage 51 is connected with the inlet 48a that sucks path 48, before the refrigeration agent of the swash plate chamber 25 that plays a role as the suction pressure district is inhaled into via rotary valve 49 among the pressing chamber 28a.That is to say that shown in the arrow of Fig. 7, the refrigeration agent in external refrigerant loop is inhaled in the swash plate chamber 25 by inlet hole P, afterwards, the communication paths of flowing through R5 arrives in the supply passage 51.Refrigeration agent in the supply passage 51 by the effect of rotary valve 49 flow through suck path 48 be inhaled into before among the pressing chamber 28a.
And when preceding cylinder thorax 28 is in the discharge stroke, when being double-head piston 30 from the stroke that moves to the left on the right side of Fig. 7, the refrigeration agent of preceding pressing chamber 28a backs down preceding expulsion valve 41a the past exhaust port 40a, is discharged among the preceding discharge chamber 13a that plays a role as the head pressure district.The not shown communication paths of flowing through refrigeration agent before being discharged among the discharge chamber 13a flows out to outside refrigerant circuit from tap hole.When back cylinder thorax 29 is in suction stroke and the refrigeration agent when discharging stroke flow identical with the 4th mode of execution.In the compressor 10 of present embodiment, adopted clack valve 46a and rotary valve 49 as the refrigeration agent suction structure, thereby can reach the effect identical with the compressor 10 of the 4th mode of execution (the 1st～the 3rd mode of execution).In addition, according to present embodiment, can obtain advantage (1), (2), the advantage (8) of the 2nd mode of execution and the identical advantage of advantage (10) of the 4th mode of execution with the 1st mode of execution.
In addition, each mode of execution can also following change.
In each mode of execution, can change the access structure of rotary valve 35,49.For example, have the occasion of poroid path, can change the diameter and the path-length of this poroid path at rotary valve 35,49.Have the occasion of groove shape path at rotary valve 35,49, can change groove depth and flute length.In addition, for example in the 3rd mode of execution shown in Figure 5, the supply passage 22b of rotary valve 35 only is made of groove shape passage portion 37.
In the 2nd～the 5th mode of execution, also can make to be arranged on the clack valve of respectively discharging chamber 13a, 14a place just the valve of expulsion valve 16a, 20a, 41a, 44a is measure-alike.
In each mode of execution, be the occasion of clack valve 18a, 46a at the refrigeration agent suction structure, also can change the discharge chamber 13a, the 14a that are arranged on protecgulum 13 or the bonnet 14 and the layout of suction chamber 13b, 14b.
In each mode of execution, also can change the layout of the inlet hole P that is connected with the external refrigerant loop.For example, inlet hole P is formed on bonnet 14.
In each mode of execution, also can change from the feed path of the inlet hole P supply system cryogen that is connected with the external refrigerant loop.For example, in each mode of execution, use bolt hole BH to suction chamber 13b, 14b supply system cryogen.But, also the other supply passage different with bolt hole BH can be set on cylinder body 11,12.
Each mode of execution is embodied in the compressor 10 of 10 cylinders, but also can change cylinder number.
As shown in Figure 3, in the 1st mode of execution, also can on running shaft 22, form the oily supply passage 60 that is communicated with the supply passage 22a of rotary valve 35.Supply passage 22a shown in Figure 3 compares the more the place ahead that extends to compressor 10 with supply passage 22a shown in Figure 1, oily supply passage 60 be formed on thrust-bearing 27 corresponding positions on.The lubricant oil that is contained in the refrigeration agent that passes through from supply passage 22a from this refrigeration agent separation and after on attached to the side face of supply passage 22a, passes through from oily supply passage 60 along with the rotation of running shaft 22.Lubricant oil in the oil supply passage 60 is supplied with to swash plate chamber 25 by thrust-bearing 27.That is, oily supply passage 60 is as being used for making lubricant oil to return the return path of swash plate chamber 25 and playing a role.Thus, can improve the lubricity of the sliding position in the swash plate chamber 25.In addition, return to swash plate chamber 25, can reduce the ratio of the oil in the external refrigerant loop of the outside that in the refrigerant circulation loop, especially is connected compressor 10, seek the raising of refrigerating capacity by making lubricant oil.In addition, reduce the oil mass that flows out to the outside of compressor 10, the oil mass that need be encapsulated in advance when making in the compressor 10 is reduced.Oil supply passage 60 also is suitable for for other mode of execution.
In each mode of execution, also can on the outer surface of the running shaft 22 that forms rotary valve 35,49, form residual refrigerant bypassing groove.Residual refrigerant bypassing groove has the path form that can remain in the pressing chamber supply of refrigeration agent when sucking end that the refrigeration agent in the pressing chamber reclaims and will reclaim when discharge finishing.That is, residual refrigerant bypassing groove forms according to the mode that the pressing chamber (cylinder thorax) of pressing chamber (cylinder thorax) when sucking end that makes when discharge finishing is communicated with.So, when the pressing chamber after discharging end is converted to suction stroke once more, can prevent that the refrigeration agent that remains in the pressing chamber from expanding once more, makes refrigeration agent to be inhaled into reliably in this pressing chamber.
Below, will from above-mentioned mode of execution and other example the technological thought that can recognize write afterwards as follows.
(1) compressed refrigeration agent is discharged in the head pressure district by the expulsion valve that is arranged between this pressing chamber and the described protecgulum in the pressing chamber of described protecgulum side, compressed refrigeration agent is discharged in the head pressure district by the expulsion valve that is arranged between this pressing chamber and the described bonnet in the pressing chamber of described bonnet side, and the valve size of the expulsion valve of described the 1st pressing chamber side is greater than the valve size of the expulsion valve of described the 2nd pressing chamber side.
Claims (5)
1. a double-headed piston type compressor is characterized in that,
Comprise:
Protecgulum (13);
Bonnet (14);
Be arranged on the cylinder body (11,12) between described protecgulum (13) and the bonnet (14), this cylinder body (11,12) has a plurality of cylinder thoraxes (28,29), and described protecgulum (13), described bonnet (14) and described cylinder body (11,12) limit swash plate chamber (25);
Suction pressure district (13b, 14b);
The double-head piston (30) of intercalation slidably in described a plurality of cylinder thoraxes (28,29), this double-head piston (30) limits the pressing chamber (28a) of described protecgulum (13) side and the pressing chamber (29a) of described bonnet (14) side, one among described two pressing chambers (28a, 29a) is the 1st pressing chamber, and another is the 2nd pressing chamber;
Rotatably supported running shaft (22) in described cylinder body (11,12);
The swash plate (24) that in described swash plate chamber (25), rotates with described running shaft (22), this swash plate (24) makes described double-head piston (30) to-and-fro motion in described cylinder thorax (28,29), its result is drawn into refrigeration agent described two pressing chambers (28a, 29a) and compresses the back and discharge in described two pressing chambers (28a, 29a) from described suction pressure district (13b, 14b);
Be used for described refrigeration agent is sucked the structure of described the 1st pressing chamber, this structure is to have the rotary valve (35,49) that described refrigeration agent is imported the importing path (22a, 22b, 47,51) of described the 1st pressing chamber from described suction pressure district (13b, 14b);
And being used for described refrigeration agent is sucked the structure of described the 2nd pressing chamber, this structure is the suction valve (18a, 46a) that opens and closes by the pressure reduction between described suction pressure district (13b, 14b) and described the 2nd pressing chamber.
2. double-headed piston type compressor as claimed in claim 1 is characterized in that,
The described pressing chamber (28a) of described protecgulum (13) side is described the 1st pressing chamber,
The described pressing chamber (29a) of described bonnet (14) side is described the 2nd pressing chamber.
3. double-headed piston type compressor as claimed in claim 1 is characterized in that,
The described pressing chamber (28a) of described protecgulum (13) side is described the 2nd pressing chamber,
The described pressing chamber (29a) of described bonnet (14) side is described the 1st pressing chamber.
4. as the described double-headed piston type compressor of arbitrary claim of claim 1～3, it is characterized in that described importing path (22b, 47,51) comprises the groove shape path of the periphery that is formed at described running shaft (22).
5. as the described double-headed piston type compressor of arbitrary claim of claim 1～3, it is characterized in that described importing path (22a) comprises the poroid path that is opened in described running shaft (22) in the mode of the end that is opened on described running shaft (22).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005302354 | 2005-10-17 | ||
| JP302354/2005 | 2005-10-17 | ||
| JP281667/2006 | 2006-10-16 |
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| Publication Number | Publication Date |
|---|---|
| CN101233319A CN101233319A (en) | 2008-07-30 |
| CN100585176C true CN100585176C (en) | 2010-01-27 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200680028005A Expired - Fee Related CN100585176C (en) | 2005-10-17 | 2006-10-17 | Double-ended piston compressor |
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| Country | Link |
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| CN (1) | CN100585176C (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| BR102019027370A2 (en) * | 2019-12-19 | 2021-06-29 | Embraco Indústria De Compressores E Soluções Em Refrigeração Ltda. | ALTERNATIVE COMPRESSOR CYLINDER COVER |
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