CN105579704A

CN105579704A - Compressor

Info

Publication number: CN105579704A
Application number: CN201380079294.5A
Authority: CN
Inventors: 田口幸彦
Original assignee: Sanden Holdings Corp
Current assignee: Sanden Corp
Priority date: 2013-09-03
Filing date: 2013-09-03
Publication date: 2016-05-11
Anticipated expiration: 2033-09-03
Also published as: DE112013007398B4; DE112013007398T5; WO2015033391A1; US20160195077A1; CN105579704B

Abstract

The invention relates to a compressor for reducing a pressure loss of a compressor caused by a suction throttle valve. The compressor (100) is equipped with: a suction chamber (141) that is annularly formed around a drive shaft (110); a suction path (104c) that is connected to the suction chamber (141); and a suction throttle valve (200) that changes the opening degree of the suction path (104c) in accordance with a pressure difference between the pressure in the suction chamber (141) and the pressure in the suction path (104c). The pressure in an area of the suction chamber (141), wherein the pressure is lower, that is away from another area of the suction chamber (141) close to the suction throttle valve (200) is introduced into the suction throttle valve (200) through a pressure introduction path (104g). Thus, the difference between the pressures before and after the suction throttle valve (200) is further increased, thereby causing the opening degree to further increase. As a result, a pressure loss at the suction throttle valve (200) is reduced, and deterioration of performance due to the provision of the suction throttle valve (200) can be suppressed.

Description

Compressor

Technical field

The present invention relates to a kind of compressor, comprise the suction throttle valve that the aperture of suction passage is changed according to the difference between the pressure of suction chamber and the pressure of suction passage.

Background technique

Patent Document 1 discloses a kind of making from evaporator outlet to the suction throttle valve that the increase and decrease of the aperture foundation refrigerant flow of the refrigerant circuit of compressor suction chamber changes.

Above-mentioned suction throttle valve is when the flow of refrigeration agent is low, by reducing from evaporator outlet to the aperture of the refrigerant circuit of compressor suction chamber, the suction pressure pulsation preventing the self-excited vibration because of compressor suction valve from producing is transmitted to vaporizer via from evaporator outlet to the refrigerant circuit of compressor suction chamber, and then produces the situation of noise.

Prior art document

Patent documentation

Patent documentation 1: Japanese Unexamined Patent Publication 2006-214396 publication

Summary of the invention

Invent technical problem to be solved

But, because suction throttle valve carries out action according to the pressure difference between the pressure (upstream side pressure, one-level side pressure) of suction passage side and the pressure (downstream side pressure, secondary side pressure) of suction chamber side, and utilize the structure that resilient member (spring) exerts a force along valve closing direction to spool, therefore, suction throttle valve produces the pressure loss, and this pressure loss becomes the main cause of the hydraulic performance decline of refrigerant circuit.

Particularly, in the compressor that suction chamber configures in the form of a ring, larger pressure distribution is produced in suction chamber, region in suction chamber near suction throttle valve is the region be connected with suction passage, therefore, this region just becomes the high region of the pressure in the region in other suction chamber of pressure ratio, and the spool of suction throttle valve in the past carries out action owing to bearing pressure the highest in above-mentioned suction chamber, therefore, the main cause that the pressure loss is expanded is become.

Thus, the object of the present invention is to provide a kind of compressor that can reduce the pressure loss caused by suction throttle valve.

The technological scheme that technical solution problem adopts

To achieve these goals, compressor of the present invention comprises: suction chamber, and above-mentioned suction chamber is formed as ring-type around live axle; Suction passage, above-mentioned suction passage is communicated with above-mentioned suction chamber; And suction throttle valve, above-mentioned suction throttle valve makes the aperture of above-mentioned suction passage change according to the pressure difference between the pressure of above-mentioned suction chamber and the pressure of above-mentioned suction passage, import path via pressure, the pressure in other region of the above-mentioned suction chamber lower than the pressure in the region away from the above-mentioned suction chamber be positioned near above-mentioned suction throttle valve is directed to above-mentioned suction throttle valve.

Invention effect

According to compressor of the present invention, using the pressure of the pressure lower than the pressure be positioned near suction throttle valve as the suction chamber acted on towards valve closing side, import to above-mentioned suction throttle valve, therefore, it is possible to reduce the pressure loss caused by suction throttle valve.

Accompanying drawing explanation

Fig. 1 is the sectional view of the compressor of embodiment of the present invention.

Fig. 2 is the figure after the part of the suction throttle valve of Fig. 1 being amplified.

Fig. 3 is the figure of the structure representing the cylinder cap shown in Fig. 1.

Fig. 4 is the sectional view of the structure of the suction throttle valve representing embodiment of the present invention.

Fig. 5 represents that the pressure of another mode of execution of the present invention imports the figure of path.

Fig. 6 is the sectional view of the assembly department of the suction throttle valve representing another mode of execution of the present invention.

Embodiment

Below, based on accompanying drawing, embodiments of the present invention are described in detail.

Fig. 1 to Fig. 3 shows the example that variable displacement compressor 100 is used as compressor.

Variable displacement compressor 100 comprises: cylinder body 101, and this cylinder body 101 is formed with multiple casing bore 101a; Front shell 102, this front shell 102 is arranged on one end of cylinder body 101; And cylinder cap 104, this cylinder cap 104 is arranged on the other end of cylinder body 101 across valve plate 103.

Live axle 110 is arranged in the mode of the transversal crankshaft room 140 formed by cylinder body 101 and front shell 102.

Swash plate 111 is configured with around the intermediate portion of the axis of live axle 110.

Swash plate 111 is connected with the rotor 112 be fixed on live axle 110 via linkage mechanism 120, and can change the inclination angle of swash plate 111 relative to live axle 110.

Linkage mechanism 120 comprises: the first arm 112a, and 112a is projecting from rotor 112 for this first arm; Second arm 111a, 111a is projecting from swash plate 111 for this second arm; And link arm 121, one end of this link arm 121 can connect relative to the first arm 112a rotationally via the first connecting pin 122, and the other end of above-mentioned link arm 121 can connect relative to the second arm 111a rotationally via the second connecting pin 123.

The shape that the through hole 111b of swash plate 111 is formed as making swash plate 111 to fascinate in the scope of inclination maximum (θ max) and minimum angle-of-incidence (θ min), is formed with the minimum angle-of-incidence limiting unit abutted with live axle 110 in through hole 111b.

The angle set of the swash plate 111 when swash plate 111 is orthogonal with live axle 110 is 0 degree (deg), the minimum angle-of-incidence limiting unit of through hole 111b is formed as making swash plate 111 inclination angle be displaced to roughly 0 degree (deg).

Inclination angle is installed between rotor 112 and swash plate 111 and reduces spring 114, reduction spring 114 in this inclination angle exerts a force towards the direction of minimum angle-of-incidence to swash plate 111, in addition, between swash plate 111 and the spring support member 116 being arranged on live axle 110, be provided with inclination angle increase spring 115, this inclination angle increases spring 115 along the direction force at inclination angle increasing swash plate 111.

At this, the applying power of the inclination angle increase spring 115 at minimum angle-of-incidence place is set as that the applying power reducing spring 114 than inclination angle is large, when live axle 110 does not rotate, swash plate 111 is positioned at inclination angle and reduces the position that applying power that the applying power of spring 114 and inclination angle increase spring 115 reaches the inclination angle of balance.

Extend to the outside of front shell 102 in the shaft sleeve part 102a that front shell 102 is run through in one end of live axle 110, be connected with not shown power transmitting deice.

In addition, between live axle 110 and shaft sleeve part 102a, be inserted with gland seal device 130, the inside of crankshaft room 140 and space outerpace are cut off.

Live axle 110 and rotor 112 are subject to bearing 131,132 along centripetal direction and support, and be subject to bearing 133, thrust plate 134 supports along thrust direction.In addition, utilize regulate screw thread 135 by live axle 110 and thrust plate 134 occur abut part and thrust plate 134 between the gap of gap adjustment for specifying.

Then, from the transmission of power of external drive source to power transmitting deice, live axle 110 and power transmitting deice synchronous rotary.

Piston 136 is configured with in casing bore 101a, in the inner space of the end of giving prominence to towards crankshaft room 140 side of piston 136, contain the peripheral part of swash plate 111, swash plate 111 links with piston 136 via a pair crawler shoe (Japanese: シュー) 137.Thus, utilize the rotation of swash plate 111 that piston 136 is moved back and forth in casing bore 101a.

Discharge chamber 142 and suction chamber 141 is formed in cylinder cap 104, wherein, above-mentioned discharge chamber 142 divides formation at the central part of cylinder cap 104 by circular division wall 104a, and above-mentioned suction chamber 141 is divided by division wall 104a and periphery wall 104b and formed, and annularly surrounds discharge chamber 142.

Suction chamber 141 is communicated with casing bore 101a via the inlet hole 103a be arranged on valve plate 103 and suction valve (not shown), and discharge chamber 142 is communicated with casing bore 101a via the tap hole 103b be arranged on valve plate 103 and expulsion valve (not shown).

Above-mentioned front shell 102, central pad (not shown), cylinder body 101, cylinder liner (not shown), valve plate 103, cylinder cover cushion (not shown) are connected by multiple stud bolt (Japanese: logical ボ Le ト) 105 with cylinder cap 104 etc., form compressor housing.

In cylinder cap 104, be formed with the suction passage 104c be communicated with suction chamber 141 in the low side refrigerant loop of refrigeration plant (such as vehicle air-conditioning systems), make suction chamber 141 be connected with the low side refrigerant loop of refrigeration plant thus.

Suction passage 104c is extended along the radial direction of live axle 110 towards suction chamber 141 from the outside of cylinder cap 104 (live axle 110).

Suction passage 104c, by with the loop-coupled inhalation port 104c1 of low side refrigerant and formed by the intercommunicating pore 104c2 that inhalation port 104c1 is connected with suction chamber 141, is configured with suction throttle valve 200 between intercommunicating pore 104c2 and suction chamber 141.

Suction throttle valve 200 carries out action according to the pressure difference between suction passage 104c (upstream side) and suction chamber 141 (downstream side), when pressure difference be below specified value, namely refrigerant flow is less time, the opening area (aperture) of suction passage 104c is contracted to minimum by suction throttle valve 200, when refrigerant flow increases, pressure difference increases and after exceeding specified value, suction throttle valve 200 makes the opening area (aperture) of suction passage 104c increase.

In addition, due to suction throttle valve 200 in the few region of refrigerant flow by suction passage 104c constriction, therefore, suppress the pressure pulsation of suction chamber 141 via low side refrigerant loop propagation to vaporizer.

In addition, discharge chamber 142 is connected with the discharge side external refrigerant loop of refrigeration plant via drain passageway 104d.Drain passageway 104d is extended towards the radially inner side of live axle 110 from the outside of cylinder cap 104, transversal suction chamber 141 and being communicated with discharge chamber 142.

Cylinder cap 104 is also provided with control valve 300.

The aperture of control valve 300 to the access 145 discharge chamber 142 be communicated with crankshaft room 140 regulates, and controls the Exhaust Gas import volume to crankshaft room 140 importing.

In addition, the refrigeration agent in crankshaft room 140 flows to suction chamber 141 via access 146, and wherein, above-mentioned access 146 is formed by access 101b, space 101c and aperture (Japanese: the オリ Off ィス) 103c be formed on valve plate 103.

Thus, by the pressure utilizing control valve 300 to change crankshaft room 140, the tilt angle of swash plate 111, the i.e. stroke of piston 136 are changed, thus variable control can be carried out to the discharge capacity of variable displacement compressor 100.

When refrigeration plant works, namely, under the state that variable displacement compressor 100 works, according to external signal, the solenoidal turn on angle be built in control valve 300 is regulated, in order to make the pressure of the suction chamber 141 imported in control valve 300 via access 104e reach specified value, change being carried out to discharge capacity and controls.

Below, with reference to Fig. 2 to Fig. 4, describe the structure of suction throttle valve 200 in detail.

Suction throttle valve 200 is made up of the first shell 201 of cylindrical shape, the second housing 204 of bottomed cylindrical, the spool 202 of bottomed cylindrical and compression helical spring 203.

First shell 201 is formed inlet opening 201a, valve seat 201b and flange 201c.

Second housing 204 has the space 204a to the cylindrical shape that spool 202 and compression helical spring 203 are accommodated, the barrel surface of second housing 204 is formed roughly pentagonal multiple exit orifice 204b towards valve seat 201b side with drift angle, and the end side 204c of second housing 204 is fitted and fixed with the periphery of the inlet opening 201a at the first shell 201.

Spool 202 is can the mode of movement vertically in the 204a of space be housed in second housing 204, between the bottom side and the bottom side of second housing 204 of the inner space of spool 202, compressive state is provided with compression helical spring 203, spool 202 exerts a force towards direction, i.e. the valve closing direction being seated at valve seat 201b by compression helical spring 203 thus.

The inner peripheral surface of the end side 204c of second housing is formed with annular recessed portion, and on the outer circumferential face of first shell 201 corresponding with this annular recessed portion, be formed with annular convex, by making above-mentioned annular recessed portion chimeric with above-mentioned annular convex, second housing 204 is fixed on the first shell 201.

In addition, the first shell 201, second housing 204 and spool 202 are plastic articles.

In addition, the outer circumferential face of the flange 201c of the first shell 201 of the end side of formation suction throttle valve 200 is formed with annular convex, this annular convex is chimeric with the annular recessed portion in the intercommunicating pore 104c2 being formed in suction passage 104c, thus is fixed in suction passage 104c suction throttle valve 200 location.

Suction throttle valve 200 is configured in the elongated area of suction passage 104c towards the mode in suction chamber 141 with exit orifice 204b.

Spool 202 has the end face 202a and cylinder outer circumferential face 202b that abut with valve seat 201b, be bearing on the cylinder inner peripheral surface of second housing 204 in slidable mode, the space 204a of cylindrical shape is divided into the first space 204a1 be communicated with suction chamber 141 by suction passage 104c and second space 204a2.

In addition, by making spool 202 move vertically in second housing 204, thus the opening area of the opening area of exit orifice 204b, i.e. suction passage 104c (aperture) is changed.

In addition, be recessed to form the groove 201d of Rack in a part of the valve seat 201b of the first shell 201, the top corner part of exit orifice 204b is communicated with the inner space of groove 201d.

Thus, when an end face 202a of spool 202 is seated at valve seat 201b, suction passage 104c is cut off completely, and suction passage 104c is communicated with suction chamber 141 via the top corner part of inlet opening 201a, groove 201d and exit orifice 204b.

The flow path area of the open area ratio groove 201d of the top corner part of exit orifice 204b when one end face 202a of spool 202 is seated at valve seat 201b is little, and the opening area of the top corner part of exit orifice 204b now becomes minimal openings area (minimum aperture).

Above-mentioned minimal openings area is set as the area that can prevent the self-excited vibration of the spool 202 occurred in the considerably less region of refrigerant flow, consider vacuumizing of variable displacement compressor 100 inside before refrigeration agent inclosure, above-mentioned minimal openings area is set as at least large than the opening area of aperture 103c value.

In addition, the diapire of second housing 204 is formed with intercommunicating pore 204d, intercommunicating pore 204d is communicated with dividing by second housing 204 and spool 202 the second space 204a2 formed with suction chamber 141.

The bottom of the second housing 204 of suction throttle valve 200 is being recessed to form collecting division wall 104a in the recess 104f of discharge chamber 142 side, and above-mentioned division wall 104a divides the discharge chamber 142 and the suction chamber 141 that are formed and be positioned at the elongated area of suction passage 104c.

In addition, import path 104g via the pressure formed in the mode of transversal discharge chamber 142 in recess 104f, be communicated with the region (the region A of Fig. 3) clipping discharge chamber 142 and be positioned at the suction chamber 141 of the side contrary with the region of the suction chamber 141 being provided with suction throttle valve 200.

Pressure import path 104g along the elongated area of suction passage 104c, i.e. the linearly formation of the radial direction of live axle 110, the opening end of the diapire side of recess 104f is configured to relative with intercommunicating pore 204d.

At this, the outer circumferential face of second housing 204 is set as less than the minimum sectional area of intercommunicating pore 104g with the sectional area in the gap 150 of the inner peripheral surface of recess 104f, gap 150 divides and forms intercommunicating pore 204d in recess 104f and pressure and import the region that path 104g is connected, and the region (the region B of Fig. 3) in suction chamber 141 near the exit orifice 204b of suction throttle valve 200.

Thus, the pressure clipping the region A of the relative suction chamber 141 in the axle center of live axle 110 imports path 104g via pressure, recess 104f and intercommunicating pore 204d acts on second space 204a2.

In addition, the sealing components such as O RunddichtringO being configured in gap 150, by arranging sealing component, the pressure of the region A of suction chamber 141 can be made more reliably to act on second space 204a2.

As mentioned above, the pressure of suction passage 104c is imported to the upstream side of spool 202 by suction throttle valve 200, the pressure of the region A of suction chamber 141 is imported to the downstream side of spool 202, along with the change of pressure difference, the i.e. circulating mass of refrigerant of above-mentioned two pressure, regulate the aperture of suction passage 104c.

The pressure difference that action occurs spool 202 is determined by the compression area of spool 202 and the applying power of compression helical spring 203, the applying power of the compression area of spool 202 and compression helical spring 203 is set to carry out valve opening action under the small pressure difference of such as about 100kPa.

In the refrigeration plant comprising the variable displacement compressor 100 with above-mentioned suction throttle valve 200, when making refrigeration agent at refrigerant circuit Inner eycle when variable displacement compressor 100 action, suction throttle valve 200 regulates along with the aperture of above-mentioned circulating mass of refrigerant to suction passage 104c, when circulating mass of refrigerant increases, increase the aperture of suction passage 104c, when circulating mass of refrigerant reduces, reduce the aperture of suction passage 104c.

Such as when refrigeration plant is for motor vehicle air-conditioning system, under the so-called high-load condition that the heat load of vehicle is larger, circulating mass of refrigerant increases, when suction chamber 141 is formed as ring-type, pressure distribution can be produced in suction chamber 141, but the region (the region B of Fig. 3) in the suction chamber 141 near suction throttle valve 200 is owing to being the region be connected with suction passage 104c, therefore be more positioned at upstream compared with other region in suction chamber 141, and become the region that pressure is the highest in suction chamber 141.

But the pressure acting on the suction chamber 141 of the spool 202 of suction throttle valve 200 is the pressure of region A, region A is positioned at the position in downstream side away from the highest region B of pressure, and the pressure of pressure ratio region B is low.

Thus, compared with acting on the suction throttle valve of spool with the pressure of the region B of suction chamber 141, the front and back pressure reduction that the pressure of the region A of suction chamber 141 acts on the spool 202 in the suction throttle valve 200 of spool 202 is larger, and makes aperture larger.Consequently, the crushing in suction throttle valve 200 reduces, and can suppress the hydraulic performance decline caused because arranging suction throttle valve 200.

In the example shown in Fig. 3, pressure is imported path 104g and be connected to the axle center and the region A place relative with the region B of the suction chamber 141 being provided with suction throttle valve 200 that clip live axle 110, the pressure of region A is imported to suction throttle valve 200 as the pressure of suction chamber 141, but import with pressure the region that path 104g is connected and be not limited to above-mentioned zone A, can be region B away from the suction chamber 141 being provided with suction throttle valve 200 and the lower region of the pressure of pressure ratio region B.

But, the region of the suction chamber 141 of pressure importing path 104g opening becomes the region of more than the low authorized pressure of pressure (such as 100kPa) of pressure ratio region B under high-load condition, particularly, by above-mentioned zone is set to the region that in suction chamber 141, pressure is minimum, thus the reduction effect of crushing can be improved.

Thus, pressure imports the structure that path 104g is not limited to the linearly formation of radial direction along live axle 110, can be formed as the structure in midway with curved part.

But, be configured with the suction chamber 141 that is formed as ring-type and be configured with in the compressor 100 of discharge chamber 142 in the inner side of this suction chamber 141, as mentioned above, one is set to the extended mode in discharge chamber 142 ground transversal in the projection of the axis of live axle 110 and cylinder cap 104 by pressure being imported path 104g, thus can when not increasing the external diameter of cylinder cap 104, short distance is liftoff is directed to suction throttle valve 200 by the pressure in region lower for the pressure away from B place, region.

When the sectional area of the suction chamber 141 of ring-type is roughly the same, the areas adjacent relative with the region B of the suction chamber 141 being provided with suction throttle valve 200, namely reach minimum farthest away from the pressure of the region A of region B, therefore, in the example shown in Fig. 3, pressure is imported path 104g and be connected with region A.

In addition, in above-mentioned suction throttle valve 200, the suction throttle valve that opening ratio under high-load condition carries out action based on the pressure of region B is large, the effect reducing pressure pulsation can have a declining tendency, but when vehicle air-conditioning systems, under high-load condition, the pressure pulsation level in the suction chamber 141 manifested as noise in compartment is lower, can not form problem actually.

In addition, when heat load diminishes, circulating mass of refrigerant reduces, consequently, pressure distribution (pressure is uneven) in suction chamber 141 reduces, therefore, the pressure of region A is close to the pressure of region B, and the aperture of suction throttle valve 200 is close to the situation of carrying out action according to the pressure of region B.

There is under the low load condition that pressure pulsation level in suction chamber 141 reduces at circulating mass of refrigerant the trend of increase, therefore, under the low load condition of reduction effect needing pressure pulsation, the reduction effect of carrying out the pressure pulsation of the situation same degree of action with the pressure according to region B can be obtained.

That is, when creating pressure distribution in suction chamber 141, in suction throttle valve 200, the pressure in the region that pressure is lower acts on spool 202, therefore, particularly under the high heat load condition of circulating mass of refrigerant increase, in the damnous situation of reduction effect not to noise in the compartment caused of pulsing because of suction pressure, the hydraulic performance decline produced by installing suction throttle valve 200 can be suppressed.

In addition, at the transversal suction chamber 141 of drain passageway 104d, and the flow path cross sectional area of suction chamber 141 is in drain passageway 104d place constriction and when forming narrow terrifically, sometimes the region A that the region that suction chamber 141 internal pressure is minimum is not relative with the region B of the suction chamber 141 being provided with suction throttle valve 200, the region AA shown in Fig. 5, namely clip suction chamber 141 narrow region AA, BB in the region AA of the B side, region away from the suction chamber 141 be arranged near suction throttle valve 200 just become the minimum region of suction chamber 141 pressure.

In this case, path 104g1 is imported towards the pressure be formed in from region B in the elongated area of suction passage 104c, formed and import path 104g2 from region AA along the pressure that the radial direction of cylinder cap 104 is extended, make pressure importing path 104g1 import path 104g2 with pressure to be communicated with, and the pressure of region AA can be made to import to suction throttle valve 200.

At this, it is extended extended to radial immediate vicinity to the radial direction in the elongated area of suction passage 104c, namely along cylinder cap 104 (live axle 110) that the pressure be communicated with the intercommunicating pore 204d of second housing 204 imports path 104g1, therefore, the region of which angular orientation no matter is positioned at away from the region that the pressure of region B is lower, extended by radially making pressure import path 104g2 from above-mentioned zone, thus path 104g can be imported by mineralization pressure.

Above, with reference to desirable mode of execution, content of the present invention is described in detail, but to those skilled in the art, has naturally known and based on basic technical conceive of the present invention and instruction, and various deformation forms can be taked.

In the example shown in Fig. 2, intercommunicating pore 204d in gap 150 division formation recess 104f and pressure import the region that path 104g is connected, and the region (the region B of Fig. 3) in suction chamber 141 near the exit orifice 204b of suction throttle valve 200, but as shown in Figure 6, the annular gap 160 between the bottom of second housing 204 and the diapire of recess 104f can be utilized, divide and form above-mentioned zone.At this, the sealing components such as O RunddichtringO can be configured in annular gap 160.

In addition, the bottom of second housing 204 can be made to abut with the diapire of recess 104f, the region utilizing the abutting part of this ring-type to divide to be formed the intercommunicating pore 204d in recess 104f and pressure to import path 104g to be connected, and the region (the region B of Fig. 3) in suction chamber 141 near the exit orifice 204b of suction throttle valve 200, in this case, above-mentioned abutting part also plays the effect of the positioning part of suction throttle valve 200.

In addition, the present invention is not limited to the structure that another side of suction throttle valve 200 (the diapire side of second housing 204) is housed in recess 104f.Such as, the plane corresponding with the diapire of second housing 204 can be formed with dividing the division wall 104a forming discharge chamber 142 and suction chamber 141, the gap between this plane and the diapire of second housing 204 is set to divide element.

In addition, the axis of suction passage 104c except can be positioned at from the radial outside of cylinder cap 104 towards suction chamber 141 with the setting the plane of the axis vertical take-off of live axle 110 except, also can be the setting of axis relative to the planar tilt of the axis vertical take-off with live axle 110 of suction passage 104c.

In addition, suction throttle valve 200 can be following structure: when an end face 202a of spool 202 is seated at valve seat 201b, do not cut off completely by suction passage 104c, but by suction passage 104c complete shut-down.

In addition, intercommunicating pore 204d, except on the diapire that can be formed in second housing 204, also can be formed in the barrel surface of the diapire of second housing 204.

In addition, compressor 100, except can being the variable displacement compressor of ramp type, also can be the variable displacement compressor of oscillation plate type.In addition, the present invention can be applied in the variable displacement compressor being provided with magnetic clutch, the clutchless type compressor without magnetic clutch, fixed capacity type reciprocating compressor and by the known various compressor such as reciprocating compressor of motoring.

(symbol description)

100 ... variable displacement compressor; 101 ... cylinder body; 102 ... front shell; 104 ... cylinder cap; 104c ... suction passage; 104g ... pressure imports path; 110 ... live axle; 141 ... suction chamber; 142 ... discharge chamber; 200 ... suction throttle valve; 201 ... first shell; 204 ... second housing; 202 ... spool; 203 ... compression helical spring.

Claims

1. a compressor, comprising:

Suction chamber, described suction chamber is formed as ring-type around live axle;

Suction passage, described suction passage is communicated with described suction chamber; And

Suction throttle valve, described suction throttle valve makes the aperture of described suction passage change according to the pressure difference between the pressure of described suction chamber and the pressure of described suction passage,

It is characterized in that,

Import path via pressure, the pressure in other region of the described suction chamber lower than the pressure in the region away from the described suction chamber be positioned near described suction throttle valve is directed to described suction throttle valve.

2. compressor as claimed in claim 1, is characterized in that,

Described compressor comprises the discharge chamber of being surrounded by described suction chamber,

In the axial projection of described driving, it is extended in the mode of transversal described discharge chamber that described pressure imports path.

3. compressor as claimed in claim 1 or 2, is characterized in that,

Described pressure imports path and the pressure in the region in the axle center and the described suction chamber relative with the region of the described suction chamber be positioned near described suction throttle valve that clip described live axle is directed to described suction throttle valve.

4. compressor as claimed in claim 1 or 2, is characterized in that,

Described suction chamber comprises the narrow of the flow path cross sectional area local constriction making described suction chamber,

Described pressure import path by clip in the region of the described narrow of described suction chamber, be directed to described suction throttle valve away from the pressure in the region of the side, region of the described suction chamber be positioned near described suction throttle valve.

5. compressor as claimed in claim 4, is characterized in that,

The drain passageway be communicated with described discharge chamber is arranged along the radial direction of described live axle in the mode of transversal described suction chamber, utilizes described drain passageway to form described narrow.

6. the compressor according to any one of claim 1 to 5, is characterized in that,

Described suction passage is extended along the radial direction of described live axle in the region in the outside of the suction chamber of described ring-type,

Described suction throttle valve comprises spool and valve shell, and described spool is accommodated into by described valve shell can along the radial displacement of described live axle,

Described pressure imports path and is communicated with the end of the radially inner side of the described live axle of described valve shell.

7. compressor as claimed in claim 6, is characterized in that,

Described valve shell is formed with the inlet opening be communicated with described suction passage in the end of the radial outside of described live axle, the exit orifice be communicated with described suction chamber is formed in intermediate peripheral wall portion, the intercommunicating pore importing communication with described pressure is formed in the end of the radially inner side of described live axle

Described spool is according to the pressure importing to the described suction chamber in described valve shell via described intercommunicating pore, and the pressure difference between the pressure importing to the described suction passage in described valve shell via described inlet opening, along the radial displacement of described live axle, change to make the opening area of described exit orifice.