CN102869885A - Compressor - Google Patents
Compressor Download PDFInfo
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- CN102869885A CN102869885A CN2011800171014A CN201180017101A CN102869885A CN 102869885 A CN102869885 A CN 102869885A CN 2011800171014 A CN2011800171014 A CN 2011800171014A CN 201180017101 A CN201180017101 A CN 201180017101A CN 102869885 A CN102869885 A CN 102869885A
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- Prior art keywords
- linking department
- valve
- support
- discharge port
- compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1009—Distribution members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/10—Adaptations or arrangements of distribution members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/10—Adaptations or arrangements of distribution members
- F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K15/00—Check valves
- F16K15/14—Check valves with flexible valve members
- F16K15/16—Check valves with flexible valve members with tongue-shaped laminae
Abstract
The disclosed compressor is provided with a discharge chamber, a compression chamber, a partition, and a discharge reed valve. The partition is provided between the discharge chamber and the compression chamber, and has an immobilized surface that faces the discharge chamber. The partition has a discharge port that can interconnect the discharge chamber and the compression chamber. The discharge reed valve contains an immobilized section, an intermediate section, and a valve section. The partition is provided with a supporting section, a receiving section, and a primary coupling section. The supporting section supports the center region of the valve section. The receiving section receives the tip region of the valve section. The primary coupling section extends from the supporting section, coupling the supporting section and the receiving section in a manner so as to bisect the tip discharge region of the discharge port. The width of the receiving section is greater than the width of the supporting section in the direction perpendicular to the lengthwise direction.
Description
Technical field
The present invention relates to compressor.
Background technique
Known just like lower compression machine (for example, patent documentation 1).In this compressor, between discharge chamber and pressing chamber, be provided with valve plate, connect at this valve plate and be provided with the discharge port that the discharge chamber can be communicated with pressing chamber.Utilization is positioned at the indoor discharge leaf valve of discharge and opens and closes discharging port.
Discharging leaf valve constitutes and comprises: fixing part, and this fixing part is being fixed with the stationary plane as the face of valve plate of discharging the opposed side in chamber; Intermediate portion, this intermediate portion extend and can lifting from fixing part along long side direction towards forward end; And valve section, this valve section opens and closes from intermediate portion along long side direction towards the forward end extension and to discharging port.Be formed with the annular slot that surrounds discharging the port complete cycle at stationary plane.In addition, the position of the stationary plane between discharge port and the annular slot forms and the valve seat surface more coplanar than the position of annular slot stationary plane more in the outer part.Under the state of discharging after leaf valve cuts out the discharge port, the front end of valve section surpasses valve seat surface in the long side direction extension.
In this type of compressor, even perfect condition is discharged port open for standing up above 0 o'clock from the difference of discharging the pressure in indoor pressure and the pressing chamber.Yet, as actual equipment, exist under the lubricated oil condition, as shown in figure 23, acting on the direction that discharge leaf valve 81 is opened in obstruction owing to connecting airtight power S, therefore until based on the power F of pressure difference overcome connect airtight power S till, discharge leaf valve 81 and can't open and discharge port 82.Under such situation, press (pressure in the pressing chamber) in the chamber as shown in figure 24.Like this, will press the phenomenon that is higher than head pressure to be called overcompression (over compression) in the chamber, thereby formed power loss.Connecting airtight power is caused by the oil film pressure of lubricant oil.Oil film pressure is compared with pressure on every side when breaking away from valve plate 27 and is become negative pressure discharging leaf valve 81 wishs.The inventor is called this effect " contrary squeezing action ".
Patent documentation 1: Japanese kokai publication hei 11-117867 communique
Because above-mentioned such power loss can cause the increase of energy consumption, therefore hope for the further reduction of power loss from the viewpoint of saving energy.
In addition, also worry the damage of discharging leaf valve for above-mentioned compressor, thus the raising of also hoping for durability.
Summary of the invention
The object of the present invention is to provide a kind of compressor, can further reduce power loss and can bring into play more excellent durability.
To achieve these goals, the inventor has carried out labor to existing compressor, and the result concentrates on the expansion of discharging port with focus and discharges the moment that leaf valve cuts out.
Namely, discharge port when observing for circular in the situation that for example overlook, because square increasing pro rata of the compression area of the valve section that this discharges port is opened and closed and the diameter of discharging port discharged port if therefore enlarge, the power of then opening the discharge port can increase.On the other hand, in this case owing to hindering the periphery that masterpiece is used for discharging port that connects airtight of the lubricant oil drive valve, therefore corresponding to the proportional situation of diameter of discharging port, discharge port and then connect airtight power and reduce if enlarge.Therefore, discharge port if enlarge, then can reduce the phenomenon of overcompression, thereby can suppress power loss.
Yet, simulation according to the inventor, when enlarging the discharge port, closing the moment of discharging leaf valve, the middle section of valve section because of the pressing chamber in inertial force or the suction process and the pressure difference of discharging the chamber (below, be called " pressure difference ") and significantly deflection in discharging port, thereby be easy to produce fatigue ruption in valve section.In the situation that compressor is easy to produce this phenomenon especially to run up.In this case, can cause the reduction of the durability of compressor.
Especially, according to this simulation, locate from intermediate portion one side in valve section with the collision of valve seat surface, stress wave is distolateral propagation forward.Therefore, overlook discharge leaf valve when observing valve section for circular situation under, the valve section of extending along long side direction towards forward end deflection and colliding intensely with stationary plane as long whip.This is that larger inertial force acts on the valve section towards the forward end of long side direction because the weight of discharge leaf valve increases towards forward end along long side direction.Make intermediate portion form the rectangular of long edge long side direction extension in order to make the discharge leaf valve open significantly the discharge port and valve section is formed in the situation of the circle more than the minor face that diameter is intermediate portion, above-mentioned phenomenon is apparent in view.
The inventor has finished the present invention in this mode.
In a mode of the present invention, provide a kind of compressor of discharging chamber, pressing chamber, spacing wall and discharging leaf valve that possesses.Described spacing wall is arranged at discharges between chamber and the pressing chamber, and has and the opposed stationary plane in discharge chamber.Described spacing wall has the discharge port that the discharge chamber can be communicated with pressing chamber.Described discharge leaf valve has length, front end, the cardinal extremity that extends along long side direction.Described discharge leaf valve comprises fixing part, intermediate portion and valve section.Described fixed position is in described cardinal extremity and be fixed in described stationary plane.Described intermediate portion extends from this fixing part to described front end and can lifting with respect to described stationary plane.Described valve section further extends from this intermediate portion to described front end and can open and close described discharge port.Described spacing wall possesses support, receiving portion and main linking department.The middle section of the described valve of described support part supports section.Described receiving portion is born the front end area of described valve section.Described main linking department more is divided into two-part mode by the front end discharging area of the discharge port of the forward end of described long side direction than described support and extends and with this support and the link of described receiving portion from described support being positioned at.Described support, described receiving portion and described main linking department arranged described spacing wall is residual, and connect and be provided with described discharge port.The width of described receiving portion with the direction of described long side direction quadrature on greater than the width of described support.
In compressor of the present invention, in the moment that the discharge leaf valve cuts out, even the middle section of valve section is wanted significantly deflection in discharging port because of inertial force, pressure difference, the also section's of the being supported supporting of the middle section of this valve section.In addition, the deflection as long whip along long side direction towards forward end of support, main linking department and receiving portion, thus can suitably support the valve section of colliding with stationary plane.Therefore, be difficult to produce fatigue ruption in valve section.
In addition, in this compressor, the width of receiving portion with the direction of long side direction quadrature on greater than the width of support.Therefore, when the valve section that discharges leaf valve and receiving portion collision, the lubricant oil on the receiving portion relaxes because the squeeze film effect makes striking force, thereby only has less effect of stress in valve section, is difficult to produce larger stress in the front end area of valve section.Therefore, discharge leaf valve and more be difficult to produce fatigue ruption, compressor can be brought into play higher durability.The squeeze film effect refers to: when reduced with speed V in parallel gap, fluid overcame the power of being extruded from the gap because having viscosity, thereby produced pressure (proportional with coefficient of viscosity and speed V).
For this compressor, under above effect, the compression area by increasing valve section and increase open the power of discharging port and reduce to hinder out valve lubricant oil connect airtight power, can reduce the phenomenon of overcompression, thereby can suppress power loss.
Thus, compressor of the present invention can further reduce power loss and can bring into play more excellent durability.
In addition, in this compressor, owing to by suppressing to discharge opening delay and can reducing to discharge pulsation of leaf valve, therefore can improve the solemn silence of compressor.And then, in this compressor, owing to having because of the minimizing of overcompression so that therefore the tendency that excitation force, bearing load and piston lateral force (transverse force) etc. reduce can reduce mechanical loss or suppress wearing and tearing.Its result, the raising that can realize economizing motorization, reliability.
In addition, in TOHKEMY 2009-235913 communique, disclose and be provided with the compressor that inhalation port integral body is divided into two-part support.Yet, comparing with the disclosed technology of the document, the present invention has following significant advantage: require harsher discharge side to play more excellent effect at aspect of performance.
If the width of support, main linking department and receiving portion is larger, the fatigue ruption that then is difficult to produce valve section.On the other hand, if the area of support, main linking department and receiving portion increases, the area of then discharging port reduces, thereby because the increase of the area of contact of support, main linking department and receiving portion causes the increase of connecting airtight power, is difficult to obtain to discharge the advantage that port is easy to open.In order to solve these conflicting problems, the present invention can suitably select size, the shape of support, main linking department and receiving portion.
Preferably, described spacing wall possesses the secondary linking department that extends from described support, and this pair linking department will be positioned at than described support and more be divided at least two-part by the cardinal extremity discharging area of the discharge port of the terminal side of described long side direction.Described support, described receiving portion, described main linking department and described secondary linking department arranged described spacing wall is residual, and connect and be provided with described discharge port.
In this case, will discharge port by support, receiving portion, main linking department and secondary linking department and be divided into the plural port of cutting apart.In this case, the intensity of support increases to some extent, and, be easy to support successively in order the valve section of deflection as long whip from the terminal side of long side direction towards forward end, thereby can effectively prevent the fatigue ruption of valve section.
Preferably, described secondary linking department extends along described long side direction.By described secondary linking department, described support, described main linking department and described receiving portion described discharge port is divided into two and cuts apart port.
In this case, be easy to realize valve section fatigue ruption prevent and be easy to open the advantage of discharging port.
Preferably, described secondary linking department, described support, described main linking department and described receiving portion have the width towards the forward end expansion of described long side direction.
In this case, can more be easy to open the discharge port at the cardinal extremity discharging area, and receiving portion more suitably bears the front end area of valve section, thereby can further prevent the fatigue ruption of valve section.
Preferably, described secondary linking department possesses: along the first secondary linking department of described long side direction extension; The the second secondary linking department that becomes the direction of 90 ° angle to extend along turning right with described main linking department; And the 3rd secondary linking department that extends of the direction that becomes 90 ° angle along turning left with described main linking department.By the described first secondary linking department, the described second secondary linking department, the described the 3rd secondary linking department, described support, described main linking department and described receiving portion described discharge port is divided into 4 and cuts apart port.
Even also be easy in this case to realize valve section fatigue ruption prevent and be easy to open the advantage of discharging port.
Preferably, described secondary linking department possesses: the first secondary linking department that becomes the direction of 120 ° angle to extend along turning right with described main linking department; And the second secondary linking department of extending of the direction that becomes 120 ° angle along turning left with described main linking department.By the described first secondary linking department, the described second secondary linking department, described support, described main linking department and described receiving portion described discharge port is divided into 3 and cuts apart port.
Even also be easy in this case to realize valve section fatigue ruption prevent and be easy to open the advantage of discharging port.
Preferably, described secondary linking department, described support, described main linking department and described receiving portion and described stationary plane are coplanar.
In this case, can suppress processing cost.
Preferably, be formed with the recess that more caves in than described stationary plane in described secondary linking department, described support, described main linking department and described receiving portion.
In this case, discharge the valve section of leaf valve and the area of contact of secondary linking department, support, main linking department and receiving portion and reduce, connect airtight power and reduce, thereby be easy to out valve.
Preferably, described recess is along the extension in the form of slot of described long side direction.
In this case, area of contact reduces, and the power of connecting airtight based on contrary extrusion effect when driving valve reduces, thereby is easy to out valve.
Preferably, described recess is along the extension in the form of slot of described width direction.
Thus, area of contact reduces.In addition, from stationary plane to secondary linking department, the delivery volume of the oil of support, main linking department and receiving portion reduces, connect airtight power and reduce, thereby be easy to out valve.
Preferably, be formed with convex surface in described secondary linking department, described support, described main linking department and described receiving portion.
In this case, discharge the valve section of leaf valve and the area of contact of secondary linking department, support, main linking department and receiving portion and also reduce, connect airtight power and reduce, thereby be easy to out valve.
Preferably, described valve section with respect to described intermediate portion also towards the Directional Extension different from described long side direction.
In this case, can easily realize enlarging the discharge port and increase the compression area of valve section.Therefore, can avoid further increasing opening the power of discharging port, and the increase of connecting airtight power that can avoid the obstruction of intermediate portion to open the lubricant oil of valve.Its result can further reduce the phenomenon of overcompression, thereby can suppress reliably power loss.In addition, in this case, the front end area of valve section more is easy to deflection as long whip and collides intensely with stationary plane.Therefore, the advantage of support, main linking department and receiving portion is more obvious.
Preferably, described stationary plane has the first slot part and the valve seat surface between described discharge port and described the first slot part to extend around the mode of described discharge port.Described valve section can with the described valve seat surface butt that is used for closing described discharge port.In the situation of overlooking the described discharge leaf valve under the state of observing after closing described discharge port, described the first slot part extends to the scope overlapping with described intermediate portion.
In this case, valve section suitably seals by valve seat surface and discharges port.
Preferably, described the first slot part is along the annular slot that circumferentially surrounds described discharge port.
In this case, close under the state after discharging port discharging leaf valve, the circular arc portion towards the terminal side of long side direction of intermediate portion and annular slot is overlapping in more wide scope.Therefore, with this overlapping area correspondingly, the area that stationary plane and intermediate portion connect airtight reduces.
Preferably, described the first slot part form except the part of the described forward end on the described long side direction with the external circumferentially upper C word shape that described discharge port is surrounded.
In this case, by enlarge C shape groove at the interval at the opposed two ends of forward end of long side direction, can easily form betwixt receiving portion.Therefore, when the valve section that discharges leaf valve and receiving portion collision, because the lubricant oil on this receiving portion can make striking force relax reliably, therefore only have less effect of stress in valve section, be difficult to produce larger stress in the front end area of valve section.Its result, this compressor can prevent from discharging the damage of leaf valve effectively, and can bring into play reliably excellent durability.
Preferably, described stationary plane have with respect to described discharge port be positioned at described long side direction terminal side the second groove and be positioned at and the overlapping scope of described intermediate portion and the connectivity slot that extends along described long side direction.In the situation of overlooking the described discharge leaf valve under the state of observing after closing described discharge port, described the second groove is crossed over the width direction of described intermediate portion and is extended.Described connectivity slot is communicated with described the first slot part with described the second slot part.
Part beyond the connectivity slot of stationary plane can become and the abutting part of discharging the leaf valve butt.
In this case, close under the state of discharging port at the discharge leaf valve, the second slot part prevents that foreign matter is clamped into intermediate portion.In addition, when opening when discharging leaf valve, the jet flow of the mixing phase that is made of gas and lubricant oil is blown the lubricant oil that clamps between intermediate portion and the stationary plane and is flown and can cut off oil film.In addition, jet flow is discharged towards the width direction outside of discharging leaf valve via connectivity slot and the second slot part from the first slot part.Therefore, can blow the lubricant oil that flies to be stranded in the first slot part, and can blow and fly the lubricant oil that is stranded in the lubricant oil between stationary plane and the intermediate portion and is stranded in the second slot part.In addition, with the partial response ground of connectivity slot, the area that stationary plane and intermediate portion connect airtight reduces.Therefore, this compressor can make stationary plane and intermediate portion from the moment arrive as early as possible, be difficult to produce the overcompression of gas.
Description of drawings
Fig. 1 is the longitudinal section of the related compressor of embodiments of the invention 1.
Fig. 2 is illustrated in to discharge leaf valve in the compressor of Fig. 1 and open the major component amplification view of discharging the state behind the port.
Fig. 3 is the plan view of choosing and illustrating valve plate and be formed with the discharge valve plate of a plurality of discharge leaf valves in the compressor of Fig. 1.
Fig. 4 is illustrated in to discharge leaf valve in the compressor of Fig. 1 and close the major component amplification plan view of discharging the state behind the port.
Fig. 5 be illustrated in discharge in the compressor of Fig. 1 leaf valve close the state of discharging behind the port, along the major component amplification view of the Z-Z line of Fig. 4.
Fig. 6 is the figure for the compressor of Fig. 1, and (A) part is the plan view of discharging port etc., and (B) part is the plan view of discharging area, and (C) part is the sectional view of support.
Fig. 7 is the plan view of discharge port of the related compressor of embodiments of the invention 2 etc.
Fig. 8 is the plan view of discharge port of the related compressor of embodiments of the invention 3 etc.
Fig. 9 is the plan view of discharge port of the related compressor of embodiments of the invention 4 etc.
Figure 10 be in the related compressor of embodiments of the invention 5 with Fig. 6 in the sectional view of the suitable support of A-A line.
Figure 11 be in the related compressor of embodiments of the invention 6 with Fig. 6 in the sectional view of the suitable support of B-B line.
Figure 12 be in the related compressor of embodiments of the invention 7 with Fig. 6 in the sectional view of the suitable support of B-B line.
Figure 13 be in the related compressor of embodiments of the invention 8 with Fig. 6 in the sectional view of the suitable support of A-A line.
Figure 14 be in the related compressor of embodiments of the invention 9 with Fig. 6 in the sectional view of the suitable support of A-A line.
Figure 15 be in the related compressor of embodiments of the invention 9 with Fig. 6 in the sectional view of the suitable support of B-B line.
Figure 16 is the figure for the related compressor of embodiments of the invention 10, and (A) part is the plan view of discharging port etc., and (B) part is the sectional view of support.
Figure 17 is illustrated in to discharge leaf valve in the related compressor of embodiments of the invention 11 and close the major component amplification plan view of discharging the state behind the port.
Figure 18 is illustrated in to discharge the major component amplification view that leaf valve cuts out the Y-Y line state of discharging behind the port, in Figure 17 in the compressor of Figure 17.
Figure 19 is illustrated in to discharge leaf valve in the related compressor of embodiments of the invention 12 and close the major component amplification plan view of discharging the state behind the port.
Figure 20 is illustrated in to discharge leaf valve in the related compressor of embodiments of the invention 13 and close the major component amplification plan view of discharging the state behind the port.
Figure 21 is illustrated in to discharge leaf valve in the related compressor of embodiments of the invention 14 and close the major component amplification plan view of discharging the state behind the port.
Figure 22 is illustrated in to discharge leaf valve in the related compressor of embodiments of the invention 15 and close the major component amplification plan view of discharging the state behind the port.
Figure 23 is in the sectional view that connects airtight power etc. of discharging leaf valve for illustration.
Figure 24 is the plotted curve that the relation between pressing in time of compressor and the chamber is shown.
Embodiment
Below, with reference to accompanying drawing the embodiment 1～15 after the present invention is specialized is described.
(embodiment 1)
Forwardly housing 3 is formed with axis hole 3a, is formed with axis hole 1b at cylinder body 1.At axis hole 3a, 1b via gland seal device 9a and radial bearing 9b, 9c and with live axle 11 supportings for rotating.Be provided with not shown belt wheel or magnetic clutch at live axle 11, be wound with engine-driven not shown band by vehicle at the belt wheel of belt wheel or magnetic clutch.
Be pressed into the flange plate (lug plate) 13 of live axle 11 in crank chamber 9 interior configurations, between flange plate 13 and front shell 3, be provided with thrust-bearing 15.In addition, live axle 11 will be disposed at swash plates 17 in the crank chamber 9 and insert logical and support this swash plate 17.Link flange plate 13 and swash plate 17 by the linkage mechanism 19 that swash plate 17 supportings can be changed for the inclination angle.
In each cylinder hole 1a, piston 21 is accommodated and carries out back and forth movement.Between cylinder body 1 and rear portion housing 5, be provided with valve cell 23.Shown in Fig. 2 amplified, this valve cell 23 possessed: with the suction valve plate 25 of the ear end face butt of cylinder body 1; With the valve plate 27 that sucks valve plate 25 butts; Discharge valve plate 29 with valve plate 27 butts; With the retaining plate 31 of discharging valve plate 29 butts.Retaining plate 31 is also used as liner.This suction valve plate 25, valve plate 27, discharge valve plate 29 and retaining plate 31 consist of valve cell 23 according to the sequential cascade that sucks valve plate 25, valve plate 27, discharge valve plate 29 and retaining plate 31.
As shown in Figure 1, front and back are provided with paired sheath (shoe) 33a, 33b between swash plate 17 and each piston 21, sheath 33a, 33b are converted to the oscillating motion of swash plate 17 back and forth movement of each piston 21 by each.
By the path 35a that bleeds crank chamber 9 is connected with suction chamber 5a, by not shown air feed path crank chamber 9 is connected with discharge chamber 5b.In the air feed channel setting not shown capacity control drive is arranged.This capacity control drive constitutes the aperture that can change according to suction pressure the air feed path.By pipe arrangement condenser is connected with discharge chamber 5b, condenser also passes through pipe arrangement via expansion valve and is connected with vaporizer, by pipe arrangement vaporizer is connected with the suction chamber 5a of compressor.Formed each pressing chamber 24 by cylinder hole 1a, piston 21 and valve cell 23.
Be formed with a plurality of inhalation port 23a that suction chamber 5a is communicated with each pressing chamber 24 at valve plate 27, discharge valve plate 29 and retaining plate 31.Be formed with a plurality of inhalation reed valve 25a that each inhalation port 23a is opened and closed at suction valve plate 25.
Shown in Fig. 2～5, be formed with a plurality of discharge port 23b that each pressing chamber 24 is communicated with discharge chamber 5b at suction valve plate 25 and valve plate 27.
Shown in (A) part of Fig. 6, with respect to each cylinder hole 1a each discharge port 23b is divided into two by support 27t described later, receiving portion 27h, main linking department 27v and secondary linking department 27w and cuts apart port 231,232.
As shown in Figure 2, be formed with a plurality of discharge leaf valve 29a that open and close respectively cutting apart port 231,232 at discharge valve plate 29.Be formed with the holder 31a that the lifting length of leaf valve 29a is respectively discharged in restriction at retaining plate 31.In the present embodiment, as shown in Figure 3, discharge a plurality of (being in the present embodiment 6) extension projection that valve plate 29 possesses circular portion and extends radially from this circular portion towards radial outside, each extends projection and has formed the discharge leaf valve 29a that each discharge port 23b is opened and closed.
Shown in Fig. 4～6, be formed with along circumferentially surrounding the circular annular slot 27a that discharges port 23b with the stationary plane 27f as the face of valve plate 27 that discharges the opposed side of chamber 5b.Annular slot 27a is an example of the first slot part of the present invention.In stationary plane 27f, being sandwiched in the circular zone of discharging between port 23b and the annular slot 27a becomes and valve seat surface (the be also referred to as glasses section) 27b more coplanar than the position of annular slot 27a stationary plane 27f more in the outer part.In this compressor, sucking valve plate 25 and valve plate 27 is spacing wall.
Shown in Fig. 2～5,6 discharge leaf valve 29a have respectively cardinal extremity and front end, and possess: fixing part 291a, this fixing part 291a are positioned at its cardinal extremity and are fixed in the stationary plane 27f of valve plate 27; Intermediate portion 292a, this intermediate portion 292a extends along the long side direction of discharging leaf valve 29a towards front end and can lifting from fixing part 291a; And the 293a of valve section, the 293a of this valve section opens and closes from intermediate portion 292a along long side direction towards the front end extension and to corresponding discharge port 23b.In the present embodiment, long side direction is parallel with stationary plane 27f and along the bearing of trend radially of live axle 11.Particularly in Fig. 4, represent to discharge the cardinal extremity of leaf valve 29a towards the long side direction of front end from each with reference character D1, represent to discharge the front end of leaf valve 29a towards the long side direction of cardinal extremity from each with reference character D2.
As shown in Figure 4, when overlooking observation intermediate portion 292a and the 293a of valve section, intermediate portion 292a forms the rectangular that long edge long side direction D1 extends towards forward end.For the 293a of valve section, take the minor face of intermediate portion 292a as diameter, and form the circle concentric with annular slot 27a.Diameter on the 293a of valve section and direction long side direction D1 quadrature is greater than the diameter along the long side direction D1 of valve seat surface 27b.
Such as Fig. 4 and shown in Figure 6, valve plate 27 possesses: the support 27t that bears the middle section of the 293a of valve section; Bear the receiving portion 27h of the front end area of the 293a of valve section; Main linking department 27v with support 27t and receiving portion 27h link; And the secondary linking department 27w that extends from support 27t.Because the 293a of valve section is circular, so the middle section of the 293a of valve section refers to comprise the constant scope at its center.The front end area of the 293a of valve section refers to be positioned at than the more forward distolateral constant scope of its middle section.Shown in (B) part of Fig. 6, will connect in the inboard discharging area A that is provided with discharge port 23b and be set in valve plate 27.The cardinal extremity discharging area A2 of semicircle that discharging area A constitutes the front end discharging area A1 of the semicircle that comprises the forward end that is positioned at long side direction D1 and is positioned at the terminal side of long side direction D1.Shown in (A) part of Fig. 6, support 27t is the constant scope that comprises the center O of discharging area A.Support 27t is configured to bear the middle section of the 293a of valve section, when observing from support 27t, discharge port 23b be present in long side direction D1 forward end about and terminal side about.Main linking department 27v extends from support 27t so that front end discharging area A1 is divided into two-part mode.Secondary linking department 27w is divided into two-part with cardinal extremity discharging area A2.And then, valve plate 27 residual support 27t, receiving portion 27h, main linking department 27v and secondary linking department 27w are arranged and connect to be provided with discharge port 23b.Owing to being provided with this support 27t, receiving portion 27h, main linking department 27v and secondary linking department 27w at valve plate 27, therefore discharging port 23b and be divided into two and cut apart port 231,232.
Shown in (A) part of Fig. 6, form: the width of support 27t, main linking department 27v and secondary linking department 27w equates in the direction with long side direction D1 quadrature, and the width of receiving portion 27h is greater than the width of support 27t, main linking department 27v and secondary linking department 27w.In addition owing to there being the restriction of the machining accuracy aspect of perforation punch process etc., therefore be not make cut apart port 231,232 bight forms the needle point fillet, but makes it slightly form circular arc.
Shown in Fig. 2～5, be formed with respect to discharging port 23b at stationary plane 27f and be positioned at the terminal side of long side direction D1 and cross over the width direction of intermediate portion 292a and the elongated slot 27c that extends.Elongated slot 27c is an example of the second slot part of the present invention.As shown in Figure 4, when overlooking when observing elongated slot 27c, elongated slot 27c is shaped as elongated ellipse with long side direction D1 quadrature.Elongated slot 27c forms darker than annular slot 27a.
In the compressor that consists of in the above described manner, by driving live axle 11 rotations, so that flange plate 13 and swash plate 17 and live axle 11 synchronous rotaries, each piston 21 carries out back and forth movement with the stroke corresponding with the tilt angle of swash plate 17 in each cylinder hole 1a.Therefore, the refrigerant gas in the suction chamber 5a is inhaled into each pressing chamber 24 and compressed, and then is discharged towards discharging chamber 5b.The lubricant oil that in compressor carries out the refrigerant gas of compression, contains the water smoke shape.This lubricant oil is clipped on the sliding parts of each piston 21, each sheath 33a, 33b and swash plate 17 etc. and suppresses the wearing and tearing of these parts.In addition, lubricant oil also is stranded in annular slot 27a and the elongated slot 27c.
During this period, as shown in Figure 2, resiliently deformable occurs because of the difference of the pressure in the discharge chamber 5b and the pressure in the pressing chamber 24 at intermediate portion 292a in discharge leaf valve 29a, and opens discharge port 23b at the 293a of valve section.As shown in Figure 5, until pressure difference overcomes connecting airtight till the power of intermediate portion 292a, the 293a of valve section can't open and discharge port 23b.
In this compressor, closing the moment of discharging leaf valve 29a, even the middle section of the 293a of valve section is wanted significantly deflection in discharging port 23b because of inertial force, pressure difference, also can utilize support 27t to come the middle section of the 293a of supporting valve section.In addition, owing to extending along long side direction D1, secondary linking department 27w, support 27t, main linking department 27v and receiving portion 27h form I word shape, therefore the intensity of support 27t increases to some extent, and along long side direction D1 towards forward end deflection as long whip, thereby be easy to from the terminal side of long side direction D1 towards forward end in order successively the 293a of valve section of suitably supporting and stationary plane 27f collision.Therefore, be difficult to produce fatigue ruption at the 293a of valve section.
Especially, in this compressor, when the 293a of valve section that discharges leaf valve 29a and receiving portion 27h collision, the lubricant oil on the receiving portion 27h relaxes because the squeeze film effect makes striking force, thereby only have less effect of stress in the 293a of valve section, be difficult to produce larger stress at the front end of the 293a of valve section.Therefore, discharge leaf valve 29a and more be difficult to produce fatigue ruption, compressor can be brought into play higher durability.
In this compressor, under above effect, by the compression area that increases the valve 293a of section increase open the power of discharging port 23b and reduce to hinder out valve lubricant oil connect airtight power, can reduce the appearance of overcompression phenomenon, thereby can suppress power loss.
Therefore, this compressor can further reduce power loss and can bring into play more excellent durability.
In addition, in this compressor, owing to by suppressing to discharge opening delay and can reducing to discharge pulsation of leaf valve 29a, therefore can also improve the solemn silence of compressor.And then, in this compressor, owing to can reduce the surge pressure in the pressing chamber 24, therefore can reduce the maximum compression load, the reliability of the slip surface of surface of contact, sheath 33a, 33b and the swash plate 17 of increase thrust-bearing 15, sheath 33a, 33b and piston 21 etc.
In addition, in this compressor, as shown in Figure 4, be formed with annular slot 27a at stationary plane 27f.Therefore, 29a closes under the state of discharging port 23b at the discharge leaf valve, and the circular arc portion 27g(of intermediate portion 292a and annular slot 27a is shown in Figure 4.) overlapping in wide scope.Therefore, with this area of overlap correspondingly, the area that stationary plane 27f and intermediate portion 292a connect airtight reduces.Therefore, can reduce the delay of opening of discharging leaf valve 29a.
And then, in this compressor, be formed with elongated slot 27c at stationary plane 27f.Therefore, 29a closes under the state of discharging port 23b at the discharge leaf valve, can prevent that foreign matter is clamped into intermediate portion 292a.
(embodiment 2)
As shown in Figure 7, in embodiment 2 compressor, combination center angle approximately fan-shaped 4 of 90 degree is cut apart port 231～234 and is consisted of and discharge port 23b.
Be formed with support 27d, main linking department 27v, receiving portion 27h and the first～3 secondary linking department 27w1～27w3 at valve plate 27.The first secondary linking department 27w1 extends along long side direction D1.The second secondary linking department 27w2 becomes the direction of 90 ° angle to extend along turning right with main linking department 27v.The 3rd secondary linking department 27w3 becomes the direction of 90 ° angle to extend along turning left with main linking department 27v.Support 27d, main linking department 27v, the secondary linking department 27w1～27w3 of receiving portion 27h and first～3rd are present in and cut apart between the port 231～234.Other structure is identical with embodiment 1 compressor.
Also can bring into play the advantage same with embodiment 1 compressor in this compressor.
(embodiment 3)
As shown in Figure 8, in embodiment 3 compressor, combination center angle approximately fan-shaped 3 of 120 degree is cut apart port 231～233 and is consisted of and discharge port 23b.
Be formed with support 27e, main linking department 27v, receiving portion 27h and the first～the second secondary linking department 27w1,27w2 at valve plate 27.The first secondary linking department 27w1 becomes the direction of 120 ° angle to extend along turning right with main linking department 27v.The second secondary linking department 27w2 becomes the direction of 120 ° angle to extend along turning left with main linking department 27v.Support 27e, main linking department 27v, receiving portion 27h and first, second secondary linking department 27w1,27w2 are present in to be cut apart between the port 231～233.Other structure is identical with embodiment 1 compressor.
Even in this compressor, also can bring into play the advantage same with embodiment 1 compressor.
(embodiment 4)
As shown in Figure 9, embodiment 4 compressor has the half moon port 231,232 of cutting apart.In addition, secondary linking department 27w, support 27i, main linking department 27v and receiving portion 27j have the width towards the forward end expansion of long side direction D1.Other structures are identical with embodiment 1 compressor.
Even in this compressor, also can bring into play the advantage same with embodiment 1 compressor.
According to the present invention, the middle section of the 293a of valve section in discharging port 23b significantly the situation of deflection reduce significantly.Therefore, the 293a of valve section may not contact with support, receiving portion, main linking department and secondary linking department whole.Therefore, can also adopt following embodiment 5～10 mode.
(embodiment 5)
In embodiment 5 compressor, as shown in figure 10, be formed with recess 27k on the surface of support 27t etc.Recess 27k forms the groove shape at the two ends of the width direction of support 27t etc.Other structure is identical with embodiment 1 compressor.
In this compressor, the area of contact of the 293a of valve section and support 27t etc. reduces, and connects airtight power to reduce, thereby is easy to out valve.In addition, according to this structure, can make support 27t etc. have certain width and keep its intensity, thereby and can suppress area of contact and suppress to connect airtight power.Other advantage is identical with embodiment 1.
(embodiment 6)
In embodiment 6 compressor, as shown in figure 11, be formed with recess 28a on the surface of support 27t etc.Recess 28a forms the groove shape along the long side direction of support 27t etc.Other structure is identical with embodiment 1 compressor.
In this compressor, area of contact reduces, and the power of connecting airtight based on contrary extrusion effect when driving valve reduces, thereby is easy to out valve.Other advantage is identical with embodiment 1.
(embodiment 7)
In embodiment 7 compressor, as shown in figure 12, be formed with the recess 27m of thinner groove shape at the two ends of the length direction of support 27t etc.Recess 27m extends along the width direction of support 27t etc.Other structure is identical with embodiment 1 compressor.
In this compressor, between valve seat surface 27b and support 27t etc., cut off the contact of lubricant oil owing to utilizing recess 27m, therefore the supply of the lubricant oil from valve seat surface 27b to support 27t etc. is cut off, the power of connecting airtight that acts between support 27t etc. and the 293a of valve section reduces, thereby is easy to out valve.Other advantage is identical with embodiment 1.
(embodiment 8)
In embodiment 8 compressor, as shown in figure 13, the recess 27n of 3 stria shapes between the recess 27s at two ends is formed at support 27t etc. with the recess 27s at two ends.Other structure is identical with embodiment 6 compressor.
In this compressor, support 27t etc. reduce with the area of contact of the 293a of valve section, connect airtight power to reduce, thereby are easy to out valve.Other advantage is identical with embodiment 1.
(embodiment 9)
In embodiment 9 compressor, such as Figure 14 or shown in Figure 15, be formed with convex surface part 27p at support 27t etc.Other structure is identical with embodiment 1 compressor.
Even in this compressor, the area of contact of the 293a of valve section and support 27t etc. also reduces, and connects airtight power to reduce, thereby is easy to out valve.Other advantage is identical with embodiment 1.
(embodiment 10)
In embodiment 10 compressor, as shown in figure 16, to enforcement shapings such as support 27t, then implement to grind, form thus a plurality of recess 27q.Other structure is identical with embodiment 1 compressor.In this compressor, also can bring into play the advantage same with embodiment 6 compressor.
(embodiment 11)
In embodiment 11 compressor, such as Figure 17 and shown in Figure 180, extend and connectivity slot 27r that annular slot 27a is communicated with elongated slot 27c is formed at stationary plane 27f towards the forward end of long side direction D1.Part beyond the connectivity slot 27r of stationary plane 27f becomes and the abutting part 27s that discharges leaf valve 29a butt.Abutting part 27s is positioned at the width direction both sides of connectivity slot 27r at stationary plane 27f, and when overlooking the discharge leaf valve 29a that observes under the state of closing discharge port 23b, this abutting part 27s and intermediate portion 292a are overlapping.In the present embodiment, the width that the width of connectivity slot 27r is set as with respect to intermediate portion 292a is about 50% to 75%, and abutting part 27s can support intermediate portion 292a reliably.
In this compressor, when opening when discharging leaf valve 29a, for the jet flow of the mixing phase that is consisted of by refrigerant gas and lubricant oil, can blow and fly and cut off oil film being installed in lubricant oil between intermediate portion 292a and the stationary plane 27f.In addition, because jet flow is discharged towards the width direction outside of discharging leaf valve 29a via connectivity slot 27r and elongated slot 27c from annular slot 27a, therefore can blow the lubricant oil that flies to be stranded in annular slot 27a, and can blow and fly the lubricant oil that is stranded in the lubricant oil between stationary plane 27f and the intermediate portion 292a and is stranded in elongated slot 27c.In addition, with connectivity slot 27r accordingly, the area that stationary plane 27f and intermediate portion 292a connect airtight reduces.Therefore, this compressor can make stationary plane 27f and the moment that intermediate portion 292a separates arrive in advance, thus the overcompression that is difficult to produce refrigerant gas.Other advantage is identical with embodiment 1.
(embodiment 12)
In embodiment 12 compressor, as shown in figure 19, the circle of the diameter that the minor face that the 293a of valve section is formed have intermediate portion 292a is above.That is, the 293a of valve section with respect to intermediate portion 292a also towards the Directional Extension different from long side direction D1.Other structure is identical with embodiment 1.
In this case, can easily enlarge the compression area of discharging port 23b and increasing the 293a of valve section.Therefore, can avoid further increasing opening the power of discharging port 23b, and the increase of connecting airtight power that can avoid the obstruction of intermediate portion 292a to open the lubricant oil of valve.Its result can further reduce the overcompression phenomenon, thereby can suppress reliably power loss.In addition, in this case, the front end towards the forward end of long side direction D1 of the 293a of valve section is easier to deflection as long whip, thereby can collide intensely with stationary plane 27f.Therefore, the advantage of support 27t etc. is more obvious.Other advantage is identical with embodiment 1.
(embodiment 13)
In embodiment 13 compressor, as shown in figure 20, employing embodiment's 4 support 27i etc. replaces embodiment 1 support 27t etc., adopts C shape groove 27c to replace embodiment 1 annular slot 27a.C shape groove 27c also is an example of the first slot part of the present invention.C shape groove 27c forms and concentric circular-arc of center O at stationary plane 27f, and except the forward end of long side direction D1, remaining part is along circumferentially discharging port 23b encirclement.The zone of stationary plane 27f that is sandwiched in the two ends opposite one another of C shape groove 27y forms receiving portion 27z with receiving portion 27j.Other structure is identical with embodiment 1.
In this case, the interval at the mutual opposed two ends by enlarging C shape groove 27y, can easily form betwixt receiving portion 27j, 27z, this receiving portion 27j, 27z form on the width direction of support 27i the other parts (part of the support 27i beyond receiving portion 27j, the 27z) greater than support 27i.Therefore, when the 293a of valve section and receiving portion 27j, 27z collision, its larger receiving portion 27j, the lubricant oil on the 27z can make striking force relax reliably, therefore only have less effect of stress in the 293a of valve section, are difficult to effectively produce larger stress at the front end of the 293a of valve section.Its result, this compressor can prevent from discharging the damage of leaf valve 29a effectively, and can bring into play reliably excellent durability.Other advantage is identical with embodiment 1.
(embodiment 14)
In embodiment 14 compressor, as shown in figure 21, employing embodiment 4 support 27i etc. replace embodiment 1 support 27t etc., adopt a pair of the first slot part 27x to replace embodiment 1 annular slot 27a.Two the first slot part 27x form and concentric circular-arc of center O at stationary plane 27f, except the forward end and terminal side of long side direction D1, remaining part from about will discharge port 23b and surround.In stationary plane 27f, the zone to each other, the opposed end of forward end of the long side direction D1 that is sandwiched at two the first slot part 27x forms receiving portion 27z with receiving portion 27j.On the other hand, in stationary plane 27f, the zone to each other, the opposed end of terminal side of the long side direction D1 that is sandwiched at two the first slot part 27x forms terminal side receiving portion 274.Other structure is identical with embodiment 1.
In this case, by forward end opposed end to each other the interval of expansion at the long side direction D1 of two the first slot part 27x, can easily form betwixt receiving portion 27j, 27z greater than other parts.Therefore, identical with embodiment 13 compressor, be difficult to effectively produce larger stress at the front end of the 293a of valve section.In addition, in this compressor, when the intermediate portion 292a that discharges leaf valve 29a and 274 collision of terminal side receiving portion, because larger terminal side receiving portion 274 only has less effect of stress in intermediate portion 292a.Its result, this compressor can prevent from discharging the damage of leaf valve 29a effectively, and can bring into play reliably excellent durability.Other advantage is identical with embodiment 1.
(embodiment 15)
In embodiment 15 compressor, as shown in figure 22, only be provided with support 27u, main linking department 27v and receiving portion 27h at valve plate 27, and adopted the discharge port 23b of U word shape.Therefore, identical with embodiment 1 support 27t, the middle section that support 27u can the 293a of supporting valve section.Other structure is identical with embodiment 1.
Even also can bring into play in this case the advantage identical with embodiment 1.
Although below 1～15 the present invention has been described in conjunction with the embodiments, the present invention is not limited to above-described embodiment 1～15, certainly can carry out suitable change in the scope that does not break away from its purport and uses.
For example, support etc. can be formed at valve plate 27 itself, and also can be formed at becomes the parts that vibration damping steel plate etc. is different from valve plate 27.
In addition, although elongated slot 27c is formed deeplyer than annular slot 27a in embodiment 1, in embodiment 11 annular slot 27a, elongated slot 27c and connectivity slot 27r are formed the identical degree of depth, the degree of depth of these grooves is not limited to this.
The present invention can be applied to air conditioner for vehicles.
Claims (16)
1. compressor is characterized in that possessing:
Discharge the chamber;
Pressing chamber;
Spacing wall, this spacing wall are arranged at discharges between chamber and the pressing chamber, and has and the opposed stationary plane in discharge chamber, and this spacing wall has the discharge port that the discharge chamber can be communicated with pressing chamber; And
Discharge leaf valve, this discharge leaf valve has length, front end, the cardinal extremity that extends along long side direction, this discharge leaf valve comprises fixing part, intermediate portion and valve section, described fixed position is in described cardinal extremity and be fixed in described stationary plane, described intermediate portion extends from this fixing part to described front end and can lifting with respect to described stationary plane, described valve section further extends from this intermediate portion to described front end and can open and close described discharge port
Described spacing wall possesses support, receiving portion and main linking department, the middle section of the described valve of described support part supports section, described receiving portion is born the front end area of described valve section, described main linking department will be positioned at than described support and more be divided into two-part by the front end discharging area of the discharge port of the forward end of described long side direction, and link from described support extension and with this support and described receiving portion
Described support, described receiving portion and described main linking department arranged described spacing wall is residual, and connect and be provided with described discharge port,
The width of described receiving portion with the direction of described long side direction quadrature on greater than the width of described support.
2. compressor according to claim 1 is characterized in that,
Described spacing wall possesses the secondary linking department that extends from described support, and this pair linking department will be positioned at than described support and more be divided at least two-part by the cardinal extremity discharging area of the discharge port of the terminal side of described long side direction,
Described support, described receiving portion, described main linking department and described secondary linking department arranged described spacing wall is residual, and connect and be provided with described discharge port.
3. compressor according to claim 2 is characterized in that,
Described secondary linking department extends along described long side direction,
By described secondary linking department, described support, described main linking department and described receiving portion described discharge port is divided into two and cuts apart port.
4. compressor according to claim 3 is characterized in that,
Described secondary linking department, described support, described main linking department and described receiving portion have the width towards the forward end expansion of described long side direction.
5. compressor according to claim 2 is characterized in that,
Described secondary linking department possesses:
The first secondary linking department along described long side direction extension;
The the second secondary linking department that becomes the direction of 90 ° angle to extend along turning right with described main linking department;
And
The 3rd secondary linking department that becomes the direction of 90 ° angle to extend along turning left with described main linking department,
By the described first secondary linking department, the described second secondary linking department, the described the 3rd secondary linking department, described support, described main linking department and described receiving portion described discharge port is divided into 4 and cuts apart port.
6. compressor according to claim 2 is characterized in that,
Described secondary linking department possesses:
The the first secondary linking department that becomes the direction of 120 ° angle to extend along turning right with described main linking department; And
The the second secondary linking department that becomes the direction of 120 ° angle to extend along turning left with described main linking department,
By the described first secondary linking department, the described second secondary linking department, described support, described main linking department and described receiving portion described discharge port is divided into 3 and cuts apart port.
7. compressor according to claim 2 is characterized in that,
Described secondary linking department, described support, described main linking department and described receiving portion and described stationary plane are coplanar.
8. compressor according to claim 2 is characterized in that,
Be formed with the recess that more caves in than described stationary plane in described secondary linking department, described support, described main linking department and described receiving portion.
9. compressor according to claim 8 is characterized in that,
Described recess is along the extension in the form of slot of described long side direction.
10. compressor according to claim 9 is characterized in that,
Described recess is along the extension in the form of slot of described width direction.
11. compressor according to claim 2 is characterized in that,
Be formed with convex surface in described secondary linking department, described support, described main linking department and described receiving portion.
12. each described compressor in 11 is characterized in that according to claim 1,
Described valve section with respect to described intermediate portion also towards the Directional Extension different from described long side direction.
13. each described compressor in 12 is characterized in that according to claim 1,
Described stationary plane has with the first slot part that extends around the mode of described discharge port and the valve seat surface between described discharge port and described the first slot part, described valve section can with the described valve seat surface butt that is used for closing described discharge port, in the situation of overlooking the described discharge leaf valve under the state of observing after closing described discharge port, described the first slot part extends to the scope overlapping with described intermediate portion.
14. compressor according to claim 13 is characterized in that,
Described the first slot part is along the annular slot that circumferentially surrounds described discharge port.
15. compressor according to claim 13 is characterized in that,
Described the first slot part form except the part of the described forward end on the described long side direction with the external circumferentially upper C word shape that described discharge port is surrounded.
16. each described compressor in 15 is characterized in that according to claim 13,
Described stationary plane have with respect to described discharge port be positioned at described long side direction terminal side the second groove and be positioned at and the overlapping scope of described intermediate portion and the connectivity slot that extends along described long side direction, in the situation of overlooking the described discharge leaf valve under the state of observing after closing described discharge port, described the second groove is crossed over the width direction of described intermediate portion and is extended, and described connectivity slot is communicated with described the first slot part with described the second slot part.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010-083872 | 2010-03-31 | ||
| JP2010083872 | 2010-03-31 | ||
| JP2011-070961 | 2011-03-28 | ||
| JP2011070961A JP5422591B2 (en) | 2010-03-31 | 2011-03-28 | Compressor |
| PCT/JP2011/058215 WO2011125835A1 (en) | 2010-03-31 | 2011-03-31 | Compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102869885A true CN102869885A (en) | 2013-01-09 |
Family
ID=44762773
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011800171014A Pending CN102869885A (en) | 2010-03-31 | 2011-03-31 | Compressor |
Country Status (7)
| Country | Link |
|---|---|
| US (1) | US20130052066A1 (en) |
| JP (1) | JP5422591B2 (en) |
| KR (1) | KR101376019B1 (en) |
| CN (1) | CN102869885A (en) |
| BR (1) | BR112012024684A2 (en) |
| DE (1) | DE112011101167T5 (en) |
| WO (1) | WO2011125835A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103016297A (en) * | 2011-09-27 | 2013-04-03 | 株式会社丰田自动织机 | Compressor |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5756737B2 (en) * | 2011-11-17 | 2015-07-29 | 株式会社豊田自動織機 | Compressor |
| TWI580867B (en) * | 2015-03-03 | 2017-05-01 | 周文三 | Improved air compressor |
| US11111827B2 (en) | 2016-10-06 | 2021-09-07 | Borgwarner, Inc. | Double flapper valve for a variable cam timing system |
| CN112682122B (en) | 2016-10-06 | 2022-09-09 | 博格华纳公司 | Dual flap valve for variable cam timing system |
| KR102612940B1 (en) * | 2017-02-03 | 2023-12-13 | 엘지전자 주식회사 | Reciprocating compressor |
| JP2023165449A (en) * | 2022-05-06 | 2023-11-16 | 三菱重工サーマルシステムズ株式会社 | compressor |
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- 2011-03-31 BR BR112012024684A patent/BR112012024684A2/en not_active IP Right Cessation
- 2011-03-31 DE DE112011101167T patent/DE112011101167T5/en not_active Ceased
- 2011-03-31 CN CN2011800171014A patent/CN102869885A/en active Pending
- 2011-03-31 KR KR1020127027899A patent/KR101376019B1/en not_active IP Right Cessation
- 2011-03-31 WO PCT/JP2011/058215 patent/WO2011125835A1/en active Application Filing
- 2011-03-31 US US13/637,570 patent/US20130052066A1/en not_active Abandoned
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Also Published As
| Publication number | Publication date |
|---|---|
| JP5422591B2 (en) | 2014-02-19 |
| US20130052066A1 (en) | 2013-02-28 |
| KR20130016316A (en) | 2013-02-14 |
| KR101376019B1 (en) | 2014-03-19 |
| DE112011101167T5 (en) | 2013-03-28 |
| BR112012024684A2 (en) | 2016-06-07 |
| JP2011226471A (en) | 2011-11-10 |
| WO2011125835A1 (en) | 2011-10-13 |
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Effective date of abandoning: 20160511 |
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