CN100410538C

CN100410538C - Capacity variable gas compressor

Info

Publication number: CN100410538C
Application number: CNB2005100889149A
Authority: CN
Inventors: 大野浩干; 石川贵志
Original assignee: KONAIK COMPRESSOR CO Ltd
Current assignee: KONAIK COMPRESSOR CO Ltd
Priority date: 2004-08-02
Filing date: 2005-08-01
Publication date: 2008-08-13
Anticipated expiration: 2025-08-01
Also published as: JP2006046094A; KR20060048898A; CN1734094A

Abstract

To provide a variable displacement type gas compressor capable of matching amount of flow-out of a part of gas in a compression stroke with desired amount precisely when the part of gas flows out selectively. In this compressor 100 (variable displacement type gas compressor) for changing volume efficiency by letting a projecting part 81 of a spool valve 80 (bypass valve) retract from a bypass hole opening part 71 opened for the inside (a compression chamber 48 (C)) of a cylinder 40, a spool valve opening position where the projecting part 81 retracts into a valve storage chamber 72 from the bypass hole opening part 71 is set in such a way that flow passage area S2 calculated by multiplying distance h between a tip face 82 of the projecting part 81 and an internal wall face 72a of the valve storage chamber 72 by peripheral length of the projecting part 81 is twice or more opening area S1 of the bypass hole opening part 71.

Description

Capacity variable gas compressor

Technical field

The present invention relates to a kind of gas compressor that changes capacity, particularly relate to a kind of operational improved capacity variable gas compressor that makes the part of the gas in the compression stroke to the bypass valve of outside outflow.

Background technique

All the time, in air is in harmonious proportion system's (to call " air-conditioning system " in the following text), the gas compressor main purpose that adopts is after the refrigerant gas compression, and this refrigerant gas is circulated in system. and, also have in this class gas compressor when discharging in the pressurized gas process, change the capacity variable gas compressor of its discharge capacity to the outside.

Illustrate, for the capacity variable type compressor that common rotary wing type compressor main body is installed in the casing, compressor main body includes and running shaft one rotor rotated; Have around rotor outer circumferential face foreign side and be the slightly cylinder of the inner peripheral surface of ovalize of section profile; And front end that should give prominence to outstanding from the outer circumferential face of rotor contacts with the inner peripheral surface of cylinder, is located at an epitrochanterian majority tabular blade with impartial angle intervals around running shaft; And 2 side components (front side member and rear side parts) of being arranged to clamp respectively this rotor and cylinder from the side of two ends of rotor face, rotation along with running shaft, the volume of the pressing chamber of dividing by 2 blades of 2 side components, rotor, cylinder and front and back setting on the sense of rotation of rotor is increased and decreased repeatedly, the refrigerant gas that sucks pressing chamber is discharged after compression.

Then, in front side member, just partly form the bypass path at the corresponding pressing chamber of compression stroke that constitutes with refrigerant gas, make refrigerant gas flow to the low-voltage space more relatively low than this compression intraventricular pressure corresponding to this compression stroke pressing chamber inside, and be provided with the guiding valve (bypass valve) that opens and closes this bypass path, by open guiding valve, make the part of refrigerant gas flow to low-voltage space from the pressing chamber that is positioned at compression stroke, capacity in the pressing chamber is reduced, and the result makes and changes from the amount of the refrigerant gas of pressing chamber discharge.

Next, with reference to Fig. 6 the structure of bypass path and guiding valve is described.

At first, bypass path 70 is by the inside that is surrounded in the face of cylinder 40, the by-pass hole opening portion 71 that is provided with opening on the end face 28 of front side member 20; Link to each other with this by-pass hole opening portion 71 and take in the valve accommodation chamber 72 of guiding valve 80 slidably; And constitute from the interconnecting part 73 that valve accommodation chamber 72 is communicated to the suction chamber 13 of low-voltage space.

The guiding valve of being taken in by valve accommodation chamber 72 80 is provided with the protuberance 81 of charging into by-pass hole opening portion 71 and having the outer circumferential face 83 that slips mutually with the side face 71a of this by-pass hole opening portion 71; And in abutting connection with this protuberance 81, and relatively outer circumferential face 83 be near normal, and the top to the internal face 72a of the valve accommodation chamber 72 that is connecting by-pass hole opening portion 71 seat surface portion 84, can be thereby reach along valve accommodation chamber 72 forward-reverses.

And, making loads on the guiding valve 80 back pressure, the protuberance 81 of guiding valve 80 is charged under the state in the by-pass hole opening portion 71 (seeing also Fig. 6 (a)), by back pressure make guiding valve 80 seat surface portion 84 with as the valve accommodation chamber internal face 72a driving fit of valve seat seat surface and seal bypass path 70.

Therefore, from be in pressing chamber 48 in the compression stroke (below, when making a general reference pressing chamber usually, annotate with symbol 48 tables, narration during, then annotate with symbol 48 (C) table with the corresponding pressing chamber of compression stroke) higher pressure refrigerant gas G just can not flow to suction chamber 13, begin compression stroke as Fig. 6 (b) expression identical time (rotary angle position of blade) like that but when not forming as yet with bypass path 70.

And, guiding valve 80 seat surface portion 84, be (state that bypass path 70 is closed) under the closed state at valve accommodation chamber internal face 72a with the valve seat seat surface, the front-end face 82 of the protuberance 81 of guiding valve 80 roughly is in same plane with the end face 28 of front side member 20.

On the other hand, under the state that does not make guiding valve 80 load back pressures, guiding valve 80 makes protuberance 81 withdraw from (Fig. 6 (c)) from by-pass hole opening portion 71 because front-end face 82 loads of protuberance 81 have the interior pressure of pressing chamber 48 in valve accommodation chamber 72 slides within.

At this moment, guiding valve 80 seat surface portion 84, leave from valve accommodation chamber internal face 72a as the valve seat seat surface, and, protuberance 81 also will retreat from valve accommodation chamber internal face 72a owing to its front-end face 82, from by-pass hole opening portion 71, keep out of the way away fully, therefore flow into the refrigerant gas G of by-pass hole opening portion 71 from pressing chamber 48, gap between the front-end face 82 by guiding valve 80 and the internal face 72a of valve accommodation chamber 72, just the track of the outer circumferential face 83 by the protuberance 81 that withdraws from from by-pass hole opening portion 71, corresponding internal face 72a from valve accommodation chamber 72 also will the cylinder week of the part of valve accommodation chamber 72 inboards the shape face imaginary plane (area S2) flow into valve accommodation chamber 72. then, refrigerant gas G flows out to suction chamber 13. from valve accommodation chamber 72 via interconnecting part 73

At this moment, as Fig. 6 (d) expression, blade 58 arrives by before the by-pass hole opening portion 71, even be positioned at formal locational pressing chamber 48 (C) as the compression stroke defined according to rotational position, because its inner refrigerant gas G constantly flows into suction chamber 13 by bypass path 70, therefore, substantial compression stroke does not begin, blade 58 has passed through the moment of by-pass hole opening portion 71, just begins substantial compression stroke.

Thereby, thereby open bypass path 70 capacity of the pressing chamber 48 (C) when compressing beginning is changed.

[patent documentation 1] Japanese patent application 2004-44398 number

Moreover say, above-mentioned capacity variable type compressor 100, make when guiding valve is after 80s to move back and open bypass path 70, the stream that refrigerant gas G is passed through when valve accommodation chamber 72 flows into from by-pass hole opening portion 71, as Fig. 4 explanatory drawing is represented, will become above-mentioned imaginary plane (by the represented planar face of cylinder week of area S2), under the flow path area S1 of area S2 that makes this imaginary plane and by-pass hole opening portion 71 condition about equally, the displacement amount of setting guiding valve 80 (promptly, the displacement amount that withdraws from from by-pass hole opening portion 71 up to protuberance 81, and total) from the front-end face 82 of protuberance 81 to the distance h of the internal face 72a of valve accommodation chamber 72.

The objective of the invention is to, as shown in Figure 4, from the inflow end (end face of front side member) of by-pass hole opening portion 71 and to the scope in outflow end (gap between the front-end face 82 of guiding valve 80 and the end face 28 of front side member), keep stable by the flow path area that makes refrigerant gas G, thereby refrigerant gas G successfully flowed out.

But, flow into by-pass hole opening portion 71 and passed through the refrigerant gas G of by-pass hole opening portion 71, owing to will move on along the bearing of trend of by-pass hole opening portion 71, arrive along its direction when the front-end face 82 of the guiding valve 80 that withdraws from, disperse towards periphery after, flow into valve accommodation chamber 72. along this front-end face 82 again by above-mentioned imaginary plane

Therefore, from the inflow part of by-pass hole opening portion 71 to valve accommodation chamber 72, play the circulation interception for refrigerant gas G, it is very difficult making the flow of this bypass path 70 guarantee to reach desirable flow. that is to say do not have to reach the refrigerant gas amount (volumetric efficiency) that compressor main body is spued and change like that according to desired.

Certainly, problem like that is not only and is appeared on the above-mentioned rotary wing type capacity variable gas compressor, even exist too on the shuttle machine of eddy type and swash plate.

Summary of the invention

The present invention be directed to a kind of design that above-mentioned situation is made, purpose is to provide a kind of capacity variable gas compressor, when a part of gas in making compression stroke flows out selectively, can make its discharge consistent with desired amount high precision.

Capacity variable gas compressor of the present invention, include compressor main body, the gas that sucks is compressed in the inside that cylinder surrounded, and the gas after this compression that spues. be formed with the bypass path in this compressor main body, make the part of the above-mentioned gas in the compression stroke flow out to low-voltage space selectively, and comprise the bypass valve that opens and closes this bypass path, switching by above-mentioned bypass valve can change the gas flow that spues. above-mentioned bypass path, by constituting: the by-pass hole opening portion of above-mentioned relatively cylinder interior opening with the bottom; Link to each other, take in the valve accommodation chamber of above-mentioned bypass valve with this by-pass hole opening portion; Be communicated to the interconnecting part of above-mentioned low-voltage space from above-mentioned valve accommodation chamber. the above-mentioned bypass valve that above-mentioned valve accommodation chamber is taken in, by constituting: charge into above-mentioned by-pass hole opening portion, and have the protuberance of the outer circumferential face that the side face with this by-pass hole opening portion slips with the bottom; With this protuberance in abutting connection with and relative above-mentioned outer circumferential face closely roughly becomes vertical and top to the internal face of the above-mentioned valve accommodation chamber that links to each other with (outstanding being contacted with) above-mentioned by-pass hole opening portion seat surface portion. the open position of the above-mentioned bypass valve that raised part withdraws to above-mentioned valve accommodation chamber from above-mentioned by-pass hole opening portion is that to set the flow path area of being calculated that amasss that makes by the girth of the front end of raised part and distance between the above-mentioned internal face and raised part for be opening area more than or equal to the above-mentioned by-pass hole opening portion on 2 times the above-mentioned cylinder wall surface.

At the upper limit more than or equal to 2 times, though there is not special provision, but, should be scope with the action effect that can embody in the present invention's design. but, from this viewpoint of movable range that should dwindle bypass valve, above-mentioned flow path area is advisable to be set near 2 times numerical value with respect to the ratio of the opening area of by-pass hole opening portion.

Here, so-called seat surface is meant towards the internal face as the valve accommodation chamber of valve seat seat surface, contact (crimping) with this internal face and stops gas discrepancy, on bypass valve formed.

As the gas that can serve as by the compressed object of the gas compressor of this capacity variable type, for instance, the refrigerant gas that resembles Freon gas and carbon dioxide etc. is all applicable, but is not to be defined in these gas.

As low-voltage space, not only can be the space outerpace of compressor main body, also can be with the cylinder interior space among the corresponding space of suction stroke (than also low) of gas corresponding to the space pressure of the stroke of feeling elated and exultant.

As compressor main body, can be the compressor main body of rotary wing type, also can be the compressor main body of eddy type, also can be the shuttle compressor main body of swash plate.

The volume-variable effect of the capacity variable gas compressor of this formation is undertaken by following elemental motion.

That is, the outer circumferential face of its protuberance of bypass valve, be with the inner peripheral surface of by-pass hole opening portion roughly corresponding shape form.And, in position that bypass valve cuts out, protuberance is charged into to the by-pass hole opening portion, the front-end face of this protuberance is in the face of the inner space of cylinder, and in abutting connection with protuberance seat surface by the top to internal face as the valve accommodation chamber of valve seat seat surface, make the locking of bypass path, thereby stop gas to flow out from the compression volume that cylinder limited by the bypass path, at this moment, from gas flow that compressor main body spued as maximum flow.

On the other hand, open position at bypass valve, protuberance moves back to the valve accommodation chamber time from the by-pass hole opening portion, bypass valve seat surface separate with the internal face (valve seat surface) of valve accommodation chamber, the part of the pressurized gas of cylinder interior, owing to flow out to low-voltage space by by-pass hole opening portion, valve accommodation chamber and interconnecting part, so, can reduce than maximum flow from the gas flow that compressor main body spued. therefore, by the switching of bypass valve, just can make the amount of the gas that spues take place actively to change.

At this, when bypass valve is positioned at the position of opening, the part of the pressurized gas in the space that cylinder limited, the flow path area of the bypass path that when flowing to low-voltage space, will pass through, for the by-pass hole opening portion, face the opening area S1 in the space (pressing chamber etc.) that cylinder limited exactly; Flow path area during from bypass tube opening portion flow valves accommodation chamber, be by and from the area of planar imaginary plane of the corresponding cylinder of the side face track of the protuberance that the by-pass hole opening portion withdraws from week, just go out according to integrating from the perimeter L of the front end of the protuberance that the by-pass hole opening portion withdraws from and distance D between the valve accommodation chamber internal face and protuberance area S2 (=D*L).

Here, common capacity variable gas compressor, the area S2 of its imaginary plane and opening area S1 are equal to setting (S1=S2), like this, if be designed to the area S2 of imaginary plane the same with opening area S1, so, then can be considered uncontrollable by the by-pass hole opening portion up to the stream of the gas of valve accommodation chamber.

Yet, flow into the by-pass hole opening portion and passed through the pressurized gas of by-pass hole opening portion, because the bearing of trend along the by-pass hole opening portion advances, when the front-end face of the protuberance that collides the bypass valve that withdraws from by its direction, immediately, disperse towards periphery to wait and flow into the valve accommodation chamber along this front-end face by above-mentioned imaginary plane.

Like this, front-end face to the protuberance of bypass valve forms the gas that impacts, because its direction of advancing is changed, so from the inflow part of this by-pass hole opening portion to the valve accommodation chamber, for gas, having played the stream impedance, is to guarantee that desired flow is very difficult with the flow nonoculture of this bypass path. that is to say that the gas flow (volumetric efficiency) that compressor main body is spued is impossible by desired the change like that.

Capacity variable gas compressor involved in the present invention, owing to set the area S2 of imaginary plane for opening area S1 more than or equal to 2 times, so, pressurized gas by the by-pass hole opening portion, for from the by-pass hole opening portion to the inflow of valve accommodation chamber part, even if make it change direct of travel, this flows into the area of part, flow path area just, because widen the opening area S1 that is set at more than or equal to 2 times by-pass hole opening portion, so, flow into part and just be difficult to form the stream impedance, thereby can be desired amount with the flow set of bypass path.

Therefore, just can make the gas flow that spues (volumetric efficiency) of compressor main body implement to change by desired amount.

And, ratio (being called opening rate) with respect to the area S2 of the imaginary plane of opening area S1, though be set at more than or equal to 200% (2 times) better, but comparatively desirable near 200%. according to inventors' of the present invention experiment, for instance, when the desired value of volumetric efficiency is set at 30% condition, opening rate is made as 200%, just can reach volumetric efficiency by 30% desired value, even the Rather, openings rate surpasses 200%, volumetric efficiency still remains on 30% state, almost do not find to change, in case opening rate surpasses 200%, need the displacement amount of unhelpful abundant assurance bypass valve on the contrary, need to enlarge the space of valve accommodation chamber.

On the other hand, if opening rate is set at 200%, the expansion in valve accommodation chamber space also can be set as irreducible minimum, and, if opening rate reaches 200% degree, need not to enlarge the space of valve accommodation chamber, also can realize by the size (length) that shortens on the relevant bypass valve movement direction.

Have, capacity variable gas compressor involved in the present invention is characterised in that the above-mentioned compressor main body is the rotary wing type compressor main body again, by constituting with the bottom: with running shaft one rotor rotated; Surround the cylinder of foreign side of the outer circumferential face of above-mentioned rotor; Outstanding from the outer circumferential face of above-mentioned rotor, this outstanding front end contacts and is installed at interval with equal angles most the tabular blades on every side of above-mentioned running shaft with the inner peripheral surface of above-mentioned cylinder; 2 side components that are respectively this rotor of clamping and above-mentioned cylinder from the side of the both ends of the surface of above-mentioned rotor and dispose; Rotation along with above-mentioned running shaft, the volume of the pressing chamber of being divided by 2 above-mentioned blades of above-mentioned 2 side components, above-mentioned rotor, above-mentioned cylinder and the alternate configuration in front and back on the sense of rotation of above-mentioned rotor is increased and decreased repeatedly, it is characterized in that above-mentioned by-pass port opening portion is formed in and reduces on the corresponding side component of compression stroke of above-mentioned compression chamber volume.

The capacity variable gas compressor of Xing Chenging according to this configuration, capacity variable gas compressor with regard to rotary wing type, the by-pass hole opening portion is arranged at this design that reduces on the corresponding side component of compression stroke of above-mentioned compression chamber volume in, suction chamber as low-voltage space, since with side component in abutting connection with being provided with, so do not need to constitute the bypass path, can constitute with short length with the path of complexity.

According to capacity variable gas compressor involved in the present invention, passed through the pressurized gas of by-pass hole opening portion, from the by-pass hole opening portion to the inflow of valve accommodation chamber part, even if make it change direct of travel, this area that flows into part is the flow path area of gas just, because widen the opening area that is set at more than or equal to 2 times by-pass hole opening portion, so, flow into part and be difficult to form the stream impedance, thereby the flow set of bypass path can be become desired amount.

Therefore, compressor main body gas discharge-amount (volumetric efficiency) is changed according to desired standard.

Via as can be known above-mentioned, the invention relates to a kind of capacity variable gas compressor, when the part of the gas that makes compression stroke flows out selectively, its discharge and desired amount are met fully.By by-pass hole opening portion with respect to inside (pressing chamber) opening of cylinder, the protuberance of guiding valve (bypass valve) is withdrawed from, in the compressor (capacity variable gas compressor) that volumetric efficiency is changed, the open position of the guiding valve that protuberance withdraws to the valve accommodation chamber from the by-pass hole opening portion is set at by the long-pending flow path area of being calculated of the girth of distance between the internal face of the front end of protuberance and valve accommodation chamber and protuberance and is the opening area more than or equal to 2 times by-pass hole opening portion.

Above-mentioned explanation only is the general introduction of technical solution of the present invention, for can clearer understanding technological means of the present invention, and can be implemented according to the content of specification, and for above-mentioned and other purposes, feature and advantage of the present invention can be become apparent, below especially exemplified by preferred embodiment, and conjunction with figs., be described in detail as follows.

Description of drawings

Fig. 1 is an embodiment's of the capacity variable gas compressor involved in the present invention sectional drawing of rotary wing type compressor.

Fig. 2 is a compressor shown in Figure 1 sectional drawing along A-A line section.

Fig. 3 is the explanatory drawing of its volume-variable mechanism of compressor shown in Figure 1, and (a) and (b) are maximum capacity; (c), (d) state for capacity is reduced.

Fig. 4 is the ideograph of the area of expression opening area and imaginary plane.

Fig. 5 is explanation opening area and the flow path area when flowing into the valve accommodation chamber and ideograph of opening rate when flowing into the by-pass hole opening portion.

Fig. 6 is the explanatory drawing of the volume-variable mechanism of existing compressor, and (a) and (b) are maximum capacity; (c), (d) state for capacity is reduced.

10 casings, 11 housings

End shield 13 suction chambers before 12

15 chamber 20 front side members that spue

28 end faces, 30 rear side parts

40 cylinders, 48 pressing chambers

48 (C) are corresponding to the pressing chamber 49a inner peripheral surface of compression stroke

50 rotors, 51 running shafts

70 bypass paths, 71 by-pass hole opening portions

72 valve accommodation chambers, 73 interconnecting parts

80 guiding valves (bypass valve), 81 protuberances

82 front-end faces, 83 outer circumferential faces

84 seat surface portion

100 compressors (capacity variable gas compressor)

G refrigerant gas R refrigerator oil

The area (flow path area) of the opening area S2 imaginary plane of S1 by-pass hole opening portion

Embodiment

Reach technological means and the effect that predetermined goal of the invention is taked for further setting forth the present invention, below in conjunction with accompanying drawing and preferred embodiment, to its embodiment of capacity variable gas compressor, structure, feature and the effect thereof that foundation the present invention proposes, describe in detail as after.

Fig. 1 is an embodiment's of the capacity variable gas compressor involved in the present invention sectional arrangement drawing of rotary wing type compressor 100, and Fig. 2 is that compressor among Fig. 1 is along the sectional drawing of A-A line section.

Illustrated compressor 100 is that the rotary wing type compressor main body is installed in capacity variable gas compressor 100 in the casing 10.Casing 10 is made of the preceding end shield 12 that at one end side forms the opening of the housing 11 of opening and this end side surface of sealing.

Be formed with the suction port 14 that sucks low pressure refrigerant gas G from the outside at preceding end shield 12 places that constitute casing 10, housing 11 places are formed with to the spue discharge opening 16 of higher pressure refrigerant gas G of outside.

Be accommodated in the compressor main body in the casing 10, by constituting with the bottom: rotor 50, rotate with running shaft 51 one; Cylinder 40, surround this rotor 50 outer circumferential face foreign side and have the section shape like oval-shaped inner peripheral surface 49a; 5 pieces of tabular blades 58, this tabular blade 58 is outstanding by the outer circumferential face of rotor 50, and the front end that this is outstanding and the inner peripheral surface 49a butt of cylinder 40 also are installed on the rotor 50 with equal angles around running shaft 51 at interval; Front side member 20 and rear side parts 30, grip roll 50 and cylinder 40 and be fixed in cylinder 40 respectively from the side of the both ends of the surface of rotor 50.

And, above-mentioned rotary wing type compressor main body is along with the rotation of running shaft 51, by by two

side components

20,30, rotor 50, cylinder 40 and 2 blades 58 on the sense of rotation of rotor, disposing by the alternate mode in front and back, the volume of 58 each pressing chamber 48 of being divided increases and decreases repeatedly, so that the refrigerant gas G. of compression, each pressing chamber 48 suction that spue

In addition, compressor main body, an end of its running shaft are supported by housing 11 by the peripheral part that makes cylinder 40, to be arranged at the setting position in the casing 10 by 12 supports of preceding end shield.

And, be accommodated at compressor main body under the state of housing 11 inside, form the chamber 15 that spues by rear side parts 30 and housing 11, on the other hand, form suction chamber 13 by front side member 20 and preceding end shield 12, here the suction chamber of being talked about 13 and the chamber 15 that spues are to adopt zero ring sealed members such as (リ Application グ) to carry out airtight isolated. in addition,, be provided with the cyclone plate of narrating in the back 60. at rear side parts 30 places

Have, the place has stored refrigerator oil R (lubricant oil) in the bottom of the chamber 15 that spues again, in order to be lubricated, to cool off, to clean and to make blade 58 described later outstanding to the direction of the inner peripheral surface 49a of cylinder 40 to the sliding position of this compressor 100 etc.

On the other hand, running shaft 51 connects the perforation supporting hole 23 at front side member 20 places and extends to the foreign side of preceding end shield 12 and at its front end place power supply portion 90 is installed via mechanical seal parts 18; The other end of running shaft 51 is by perforation bearing hole 32 supportings of rear side parts 30.

Have at rotor 50 places and to be 5 blade grooves 56 that are the narrow slit shape radial and that form at interval with equal angles around the rotating center of rotor 50; At these blade groove 56 places, be inserted with planar blade 58. respectively

Each blade 58, rotation by rotor 50 produces centrifugal force, and utilize the oil pressure of the refrigerator oil R in the drawn fixed back pressure chamber in the bottom be added into blade groove 56 and blade 58, direction to the inner peripheral surface 49a of cylinder 40 is outstanding, the front end that this blade 58 is given prominence to is contacting state and by the application of force with the inner peripheral surface 49a of cylinder 40.

For this reason, the inner space of cylinder 40 is divided into small chamber by cylinder 40, rotor 50, blade 58, front side member 20 and rear side parts 30, and this each small chamber has formed pressing chamber 48 and carried out the variation of volume along with the rotation of rotor 50 repeatedly.

Have, front side member 20 place's openings have the front side suction port, suction chamber 13 are communicated with pressing chamber 48 again; The refrigerant gas G that flows into suction chamber 13 is inhaled in the pressing chamber 48 by the front side suction port.

On the other hand, can also form rear side suction portion at rear side parts 30 places. for the compressor 100 of this rear side suction of formation portion, need at cylinder 40 places formation intercommunicating pore, this rear side suction portion is communicated with the front side suction port.

So, in this rear side suction portion, just can supply order through the refrigerant gas G of the intercommunicating pore of front side suction port, cylinder 40,, performance same with the front side suction port makes refrigerant gas G suck the effectiveness of pressing chamber 48.

At the cyclone plate 60 that 15 places, chamber that spue of rear side parts 30 are provided with, this cyclone plate 60 possesses oil separator 62 is arranged, uses so that the refrigerator oil R that sneaks among the refrigerant gas G separates.

Cylinder 40 places are formed with the chamber 44 that spues.And the part place by the cylinder 40 of thin-walled property that is formed in this chamber 44 that spues offers discharge opening 42, in order to be communicated with the pressing chamber 48 and the chamber 44 that spues.

These discharge opening 42 places are provided with the pilot valve of opening to chamber 44 1 sides that spue 43 (valve body 43a and valve seat 43b).And the higher pressure refrigerant gas G that spues to the chamber 44 that spues by discharge opening 42, pilot valve 43 from pressing chamber 48, spues to the chamber 15 that spues through the oil separator 62 of cyclone plate 60 at the intercommunicating pore (not having diagram) that forms via rear side parts 30 places.

At this,, drop onto the bottom of the chamber 15 that spues and store in this bottom by the refrigerator oil R that oil separator 62 separates.

Have again, for realize making blade 58 at the pressure feed of the internal face application of force of cylinder to the purpose and the lubricated running shaft 51 of blade groove 56 with connect purpose between the bearing hole 32, the delivery apparatus that the refrigerator oil R that this compressor 100 possesses has the bottom with the chamber 15 that spues to store dredges to each position.

That is to say, form the sensible oil circuit 33 that connects bearing hole 32 at rear side parts 30 places, and, be provided with recess (smooth groove) 35 in end towards the rear side parts 30 of rotor 50, from being positioned at the opening of the oil circuit 33 that connects bearing hole 32, be communicated with blade groove 56 with micro-gap between the running shaft 51 by connecting bearing hole 32.

This recess 35 is as the double dot dash line among Fig. 2 is represented, be arranged to the almost fan shape respectively.And this recess 35 is formed at the position that is communicated with the back pressure chamber of the blade groove 56 of rotor 50.Have, place, the necking section of recess 35 further is formed with the little recess that is used to dredge high pressure refrigerator oil R so that for the blade groove 56 that constitutes the pressing chamber 48 corresponding with the latter end of compression stroke, still can play the effect of lifting oil pressure again.

In addition, place, the bottom of cylinder 40 is provided with openings 46, in order to connect the oil circuit 33 of rear side parts 30; Be formed with oil circuit (do not have diagram) at front side member 20 places, in order to the lateral opening of the front side member 20 that is communicated with this openings 46 with connect supporting hole 23.Refrigerator oil R dredges refrigerator oil R via the positions such as recess (smooth groove) 25 that connect micro-gap between supporting hole 23 and the running shaft 51, form to the face place towards rotor 50 of front side member 20.

Have again, this compressor 100, owing to be to change to the spue gas compressor of capacity variable type of gas flow of refrigerant gas G of outside, so, as shown in Figure 2, the inside at front side member 20, the formation pressing chamber 48 corresponding with the compression stroke of refrigerant gas G (below, when making a general reference pressing chamber usually, annotate with symbol 48 tables; When narrating the pressing chamber corresponding with compression stroke, label symbol 48 (C) then) part place, be formed with bypass path 70, the inner refrigerant gas G of pressing chamber 48 (C) of this compression stroke correspondence is flowed out in the suction chamber 13 of the low-voltage space that the interior pressure of this pressing chamber 48 (C) also will be low relatively, and be provided with guiding valve 80 (bypass valve), in order to open and close bypass path 70, by open guiding valve 80, make the part of the refrigerant gas G of pressing chamber 48 (C) flow out to suction chamber 13, capacity in the pressing chamber 48 (C) is reduced, consequently, make the discharge-amount of the refrigerant gas G that spues to the chamber 44 that spues from pressing chamber 48 (C) change.

Below, in conjunction with Fig. 3, the structure of bypass path 70 and guiding valve 80 is elaborated. and, (a) of Fig. 3, (c) be with shown in Fig. 1 laterally and the pressing chamber 48 (C) of row arrangement and the schematic representation that front side member 20 becomes vertical arrangement. (a) represent to be the high pressure refrigerator oil R that supplied with from through hole 46 (with reference to Fig. 1) close the state of bypass path 70 by guiding valve 80 being applied back pressure, guiding valve 80; (c) expression is by making blocking outflow so that this back pressure of not loading is opened the state of bypass path 70.

At first, the inside that bypass path 70 is surrounded in the face of cylinder 40, bypass path 70 comprises: the by-pass hole opening portion 71 that forms opening at end face 28 places of front side member 20; Be connected, slidably take in the valve accommodation chamber 72 of guiding valve 80 with this by-pass hole opening portion 71; And the interconnecting part 73. that leads to suction chamber 13 from valve accommodation chamber 72

The guiding valve 80 that valve accommodation chamber 72 is taken in comprises: external 83 the protuberance 81 of charging into by-pass hole opening portion 71 and slipping with the side face 72a with this by-pass hole opening portion 71; With this protuberance 81 in abutting connection with, and relative outer circumferential face 83 roughly becomes vertical and push up to the internal face 72a of the valve accommodation chamber 72 that is connecting by-pass hole opening portion 71 seat surface portion 84, move thereby can advance and retreat along valve accommodation chamber 72.

Then, guiding valve 80 load back pressures, the protuberance 81 that makes guiding valve 80 under the state of charging into by-pass hole opening portion 71 (Fig. 3 (a)), by back pressure, guiding valve 80 seat surface portion 84 connect airtight as the valve accommodation chamber internal face 72a of valve seat seat surface and close bypass path 70.

Therefore, just can not flow out to suction chamber 13. shown in Fig. 3 (b) from the higher pressure refrigerant gas G of pressing chamber 48 (C), the time identical when not forming with bypass path 70 begins compression stroke.

Have again, guiding valve 80 seat surface portion 84, with state as the valve accommodation chamber internal face 72a crimping (bypass path 70 closing state) of valve seat seat surface under, the front-end face 82 of the protuberance 81 of guiding valve 80 roughly forms same plane with the end face 28 of front side member 20.

On the other hand, under guiding valve 80 is not loaded the state of back pressure, the interior pressure of the pressing chamber 48 that guiding valve 80 is loaded by the front-end face 82 of protuberance 81, in the slides within (Fig. 3 (c)) of valve accommodation chamber 72 so that protuberance 81 withdraws from from by-pass hole opening portion 71.

At this moment, guiding valve 80 seat surface portion 84, leave valve accommodation chamber internal face 72a as the valve seat seat surface, and, move back valve accommodation chamber 72 one rear flank of protuberance 81 its front-end faces 82 after also will lean on than valve accommodation chamber internal face 72a, break away from from by-pass hole opening portion 71 fully, therefore the refrigerant gas G that flows into by-pass hole opening portions 71 from pressing chamber 48 gap between the internal face 72a of the front-end face 82 by guiding valve 80 and valve accommodation chamber 72 just, just schematic representation Fig. 4 is represented, by track according to the outer circumferential face 83 of the protuberance 81 that withdraws from from by-pass hole opening portion 71, corresponding internal face 72a from valve accommodation chamber 72 also will the cylinder week of the part of valve accommodation chamber 72 inboards the shape face imaginary plane (area S2) flow into valve accommodation chamber 72. then, refrigerant gas G flows out to suction chamber 13. from valve accommodation chamber 72 via interconnecting part 73

In this case, shown in Fig. 3 (d), blade 58 arrives by before the by-pass hole opening portion 71, for instance, even according to rotational position, be positioned at defined as the formal locational pressing chamber 48 (C) of compression stroke, because its inner refrigerant gas G still can constantly flow out in the suction chamber 13, therefore via bypass path 70, substantial compression stroke does not begin, and blade 58 has passed through the beginning that the moment of by-pass hole opening portion 71 becomes substantial compression stroke.

Therefore, open the 70 substantial elapsed times that delay compression stroke of meeting of bypass path, thereby the capacity of the pressing chamber 48 (C) when compressing beginning changed.

Then, the angular orientation that is provided with about the bypass path 70 of the sense of rotation of rotor 50, the capacity of the pressing chamber 48 (C) when beginning according to compression stroke can be tried to achieve in advance by calculating, and can be set out the amount that makes its refrigerant gas G that spues from discharge opening 42.

Yet, the compressor 100 of above-mentioned capacity variable type, make when guiding valve is after 80s to move back and open bypass path 70, refrigerant gas G from by-pass hole opening portion 71 to the process that valve accommodation chamber 72 flows into the stream of process, just form above-mentioned imaginary plane, but compressor 100 concerning present embodiment, the area S2 of this imaginary plane, will be by 2 times of the flow path area S1 that sets by-pass hole opening portion 71 for (percentage (opening rate) to the area S2 of the imaginary plane of opening area S1 be 200%), set guiding valve 80 displacement amount (protuberance 81 from by-pass hole opening portion 71 up to the displacement amount that withdraws from and, total from the front-end face 82 of protuberance 81 to the distance h of the internal face 72a of valve accommodation chamber 72).

The area S2 that existing compressor is considered to above-mentioned imaginary plane sets the displacement amount of guiding valve 80 usually by the amount that is equal to opening area S1 (percentage (opening rate) of the area S2 of opening area S1 imaginary plane is 100% relatively). concerning existing compressor, inflow end (end face of front side member 20) from by-pass port opening portion 71, via outflow end (gap between the front-end face 82 of guiding valve 80 and the end face 28 of front side member 20), be made as certain value by flow path area S, refrigerant gas G will successfully be flowed out refrigerant gas G.

But, in fact, flow to by-pass hole opening portion 71 and passed through the refrigerant gas G of by-pass hole opening portion 71, owing to will move on along the direction that by-pass hole opening portion 71 is extended, after colliding the front-end face 82 of protuberance 81 of the guiding valve 80 that withdraws from along its direction, scatter towards periphery etc., flow into valve accommodation chamber 72. by above-mentioned imaginary plane along this front-end face 82

Therefore, from the inflow part of by-pass hole opening portion 71 to valve accommodation chamber 72, for refrigerant gas G, played the effect of circulation impedance, concerning existing compressor, it is very difficult making the flow of this bypass path 70 guarantee to reach desired flow. also just say that to the amount (volumetric efficiency) of the refrigerant gas that compressor main body spued, it is impossible making it be reduced to by calculating desired level in advance.

But, compressor 100 in the present embodiment, displacement by guiding valve 80, from by-pass hole opening portion 71 to the inflow of valve accommodation chamber 72 part, the area S2 of above-mentioned imaginary plane just, owing to be set at 2 times of by-pass hole opening portion 71 its opening area S1, so, circuit portion just is difficult to form the stream impedance, and the flow that can make bypass path 70 guarantees to reach desired flow. promptly, to the amount (volumetric efficiency) of the refrigerant gas that compressor main body spued, it is reduced to by calculating desired desired value in advance.

Here, Fig. 5 represents the chart of the experimental example that concerns between opening rate that inventors of the present invention implement and the volumetric efficiency. this caption, when opening guiding valve 80, installing by-pass hole opening portion 71 on the angular orientation of the volumetric efficiency 30% on calculating, with the opening rate from 0% to 350%, by 50% being unit, the variation of the volumetric efficiency of resulting reality.

According to this experimental result, for the opening rate 100% that existing compressor was suitable for, with respect to the volumetric efficiency 30% on calculating, in fact, obtain about 40% volumetric efficiency only, with respect to this,, can realize volumetric efficiency by the desired value 30% on calculating from the opening rate 200% that the compressor 100 of present embodiment is suitable for.

And, according to this experimental result, even surpass 200% opening rate, confirmed that volumetric efficiency still passes with 30% state. and, along with the expansion of opening rate, confirmed to need to enlarge the displacement amount of guiding valve 80, but, since obtain desired volumetric efficiency, that is petty, and the opening rate of maintenance 200% is very important, so, for the compressor 100 of present embodiment, the displacement amount of guiding valve 80 increased be controlled at inferior limit, just can obtain desired volumetric efficiency.

Like this, according to the related compressor 100 of present embodiment,, the gas flow that spues (volumetric efficiency) of compressor main body is changed by desired amount by the switching of guiding valve 80.

And, the compressor 100 that present embodiment is related, compressor main body is a rotary wing type, by-pass hole opening portion 71 is formed at and the corresponding front side member of compression stroke 20 places that reduce the capacity of pressing chamber 48, as the suction chamber 13 of low-voltage space, owing to be provided with front side member 20 adjacency, so, do not need to constitute bypass path 70, can constitute with short length with the path of complexity.

In addition, the compressor 100 of the above embodiments, compressor main body is the gas compressor of rotary wing type, but, capacity variable gas compressor involved in the present invention, compressor main body is not to be defined in this kind form, for the capacity variable gas compressor that includes scroll compressor main body and swash plate reciprocal compressor main body, and also can be suitable equally.

The above, it only is preferred embodiment of the present invention, be not that the present invention is done any pro forma restriction, though the present invention discloses as above with preferred embodiment, yet be not in order to limit the present invention, any those skilled in the art, in not breaking away from the technical solution of the present invention scope, when the technology contents that can utilize above-mentioned announcement is made a little change or is modified to the equivalent embodiment of equivalent variations, in every case be the content that does not break away from technical solution of the present invention, according to technical spirit of the present invention to any simple modification that above embodiment did, equivalent variations and modification all still belong in the scope of technical solution of the present invention.

Claims

1. capacity variable gas compressor, it comprises compressor main body, the gas that sucks is compressed in the inside that cylinder surrounded and this pressurized gas that spues, be formed with the bypass path in this compressor main body, make the part of the above-mentioned gas in the compression stroke flow out to low-voltage space selectively, and comprise the bypass valve that opens and closes this bypass path, the switching by above-mentioned bypass valve can change the gas flow that spues, it is characterized in that

Above-mentioned bypass path comprises: the by-pass hole opening portion that the inside formation opening of above-mentioned relatively cylinder is arranged; Be connected, take in the valve accommodation chamber of above-mentioned bypass valve with this by-pass hole opening portion; And the interconnecting part that is communicated to above-mentioned low-voltage space from above-mentioned valve accommodation chamber;

Be accommodated in the above-mentioned bypass valve of above-mentioned valve accommodation chamber, comprise: charge into above-mentioned by-pass hole opening portion and have the protuberance of the outer circumferential face that the side face with this by-pass hole opening portion slips; And roughly become vertically in abutting connection with this protuberance and with respect to above-mentioned outer circumferential face, and the top to the internal face of the above-mentioned valve accommodation chamber that is connecting above-mentioned by-pass hole opening portion seat surface portion;

Raised part is to set the long-pending flow path area of being calculated that makes by the girth of the front end of raised part and distance between the above-mentioned internal face and raised part for to be the opening area more than or equal to the above-mentioned by-pass hole opening portion on 2 times the above-mentioned cylinder wall surface from above-mentioned by-pass hole opening portion to the open position of the above-mentioned bypass valve that above-mentioned valve accommodation chamber withdraws from.

2. capacity variable gas compressor according to claim 1 is characterized in that the above-mentioned compressor main body is the rotary wing type compressor main body, is provided with and running shaft one rotor rotated; Surround the cylinder of foreign side of the outer circumferential face of above-mentioned rotor; Outstanding from the outer circumferential face of above-mentioned rotor, this outstanding front end contacts and is installed at interval with equal angles most the tabular blades on every side of above-mentioned running shaft with the inner peripheral surface of above-mentioned cylinder; And be arranged to from the side of the both ends of the surface of above-mentioned rotor 2 side components of this rotor of clamping and above-mentioned cylinder respectively; Along with the rotation of above-mentioned running shaft, the volume of the pressing chamber of being divided by 2 above-mentioned blades of above-mentioned 2 side components, above-mentioned rotor, above-mentioned cylinder and the alternate configuration in front and back on the sense of rotation of above-mentioned rotor is increased and decreased repeatedly;

Above-mentioned by-pass port opening portion is formed on and the corresponding side component of the compression stroke place that reduces above-mentioned compression chamber volume.