WO2011125835A1

WO2011125835A1 - Compressor

Info

Publication number: WO2011125835A1
Application number: PCT/JP2011/058215
Authority: WO
Inventors: 隆宏諸井; 正和大林; 直文木村; 文太吉住; 黒石　真且; 近藤　靖裕; 吉田　一徳
Original assignee: 株式会社豊田自動織機; 株式会社豊田中央研究所
Priority date: 2010-03-31
Filing date: 2011-03-31
Publication date: 2011-10-13
Also published as: CN102869885A; DE112011101167T5; US20130052066A1; BR112012024684A2; KR20130016316A; JP2011226471A; KR101376019B1; JP5422591B2

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

Compressor

The present invention relates to a compressor.

The following compressors are known (for example, Patent Document 1). In this compressor, a valve plate is provided between the discharge chamber and the compression chamber, and a discharge port that allows communication between the discharge chamber and the compression chamber is provided through the valve plate. The discharge port is opened and closed by a discharge reed valve located in the discharge chamber.

The discharge reed valve includes a fixed portion fixed to a fixed surface that is a surface of the valve plate facing the discharge chamber, an intermediate portion that extends from the fixed portion to the distal end side along the longitudinal direction, and can be lifted. And a valve portion that extends to the tip side along the longitudinal direction to open and close the discharge port. An annular groove surrounding the entire circumference of the discharge port is formed on the fixed surface. The portion of the fixed surface between the discharge port and the annular groove forms a flush valve seat surface with the portion of the fixed surface outside the annular groove. When the discharge reed valve closes the discharge port, the tip of the valve portion extends beyond the valve seat surface in the longitudinal direction.

In this type of compressor, it is ideal to open the discharge port immediately after the difference between the pressure in the discharge chamber and the pressure in the compression chamber exceeds zero. However, when the lubricating oil is present as in the actual machine, the contact force S acts in a direction that prevents the opening of the discharge reed valve 81 as shown in FIG. 23, so that the force F due to the pressure difference overcomes the contact force S. Until then, the discharge reed valve 81 does not open the discharge port 82. In such a situation, the bore internal pressure (pressure in the compression chamber) is as shown in FIG. The phenomenon in which the bore internal pressure becomes higher than the discharge pressure in this way is called over-compression, which results in power loss. The adhesion is due to the oil film pressure of the lubricating oil. The oil film pressure is more negative than the surrounding pressure when the discharge reed valve 81 is about to leave the valve plate 27. The inventors refer to this action as a “reverse squeeze action”.

Japanese Patent Laid-Open No. 11-117867

Since the power loss as described above causes an increase in energy consumption, further reduction of the power loss is required from the viewpoint of energy saving.

Also, in the above compressor, there is a concern about the damage of the discharge reed valve, and there is a demand for improved durability.

An object of the present invention is to provide a compressor capable of further reducing power loss and exhibiting superior durability.

In order to achieve the above object, the inventors focused on the expansion of the discharge port and the moment when the discharge reed valve closes as a result of detailed analysis of the conventional compressor.

That is, when the discharge port is circular in plan view, for example, the pressure receiving area of the valve portion that opens and closes the discharge port increases in proportion to the square of the diameter of the discharge port. The power to open is increased. On the other hand, in this case, the adhesion force of the lubricating oil that hinders valve opening acts on the periphery of the discharge port, and therefore is only proportional to the diameter of the discharge port. If the discharge port is enlarged, the adhesion force becomes smaller. For this reason, if the discharge port is enlarged, over-compression can be reduced, and power loss can be suppressed.

However, according to the simulation by the inventors, when the discharge port is enlarged, the central region of the valve portion is an inertial force at the moment when the discharge reed valve is closed, or the pressure difference between the compression chamber and the discharge chamber in the suction process (hereinafter, It is greatly bent in the discharge port due to “pressure difference”, and the valve portion is likely to be fatigued. This tendency is particularly likely when the compressor is operated at high speed. In this case, the durability of the compressor is reduced.

Particularly, according to the simulation, in the valve portion, the collision with the valve seat surface starts from the intermediate portion side, and the stress wave is propagated toward the tip side. For this reason, when the valve portion of the discharge reed valve is circular in plan view, the valve portion extending toward the distal end along the longitudinal direction bends like a whip and collides violently with the fixed surface. This is because the weight of the discharge reed valve increases toward the distal end side along the longitudinal direction, and a large inertia force acts on the valve portion toward the distal end side in the longitudinal direction. This phenomenon is conspicuous when the middle part has a rectangular shape with the long side extending in the longitudinal direction and the valve part has a circular shape with a diameter equal to or larger than the short side of the middle part so that the discharge reed valve greatly opens the discharge port.

The inventors have thus completed the present invention.

In one aspect of the present invention, a compressor including a discharge chamber, a compression chamber, a partition wall, and a discharge reed valve is provided. The partition wall is provided between the discharge chamber and the compression chamber, and has a fixed surface facing the discharge chamber. The partition has a discharge port capable of communicating the discharge chamber and the compression chamber. The discharge reed valve has a length extending along the longitudinal direction, a distal end, and a proximal end. The discharge reed valve includes a fixed portion, an intermediate portion, and a valve portion. The fixing portion is positioned on the base end and fixed to the fixing surface. The intermediate portion extends from the fixed portion toward the tip and can be lifted with respect to the fixed surface. The valve portion further extends from the intermediate portion toward the tip and can open and close the discharge port. The partition includes a support portion, a receiving portion, and a main connection portion. The support portion supports a central region of the valve portion. The receiving part receives a tip region of the valve part. The main connecting portion extends from the support portion to connect the support portion and the receiving portion so as to bisect the tip discharge region of the discharge port located on the tip end side in the longitudinal direction from the support portion. The discharge port is penetrated through the partition so as to leave the support portion, the receiving portion, and the main connecting portion. The width of the receiving portion is larger than the width of the support portion in a direction orthogonal to the longitudinal direction.

In the compressor according to the present invention, even when the discharge reed valve is closed, even if the central region of the valve portion tends to be largely bent into the discharge port due to inertia force or pressure difference, the central region of the valve portion is supported by the support portion. Further, the support portion, the main connecting portion, and the receiving portion can suitably support the valve portion that collides with the fixed surface while being bent like a whip toward the distal end side along the longitudinal direction. For this reason, it is hard to produce fatigue failure in a valve part.

In this compressor, the width of the receiving portion is larger than the width of the supporting portion in the direction orthogonal to the longitudinal direction. For this reason, when the valve part of the discharge reed valve collides with the receiving part, the lubricating oil on the receiving part relaxes the collision force due to the squeeze film effect, and only a small stress acts on the valve part. Large stress is unlikely to occur. For this reason, the discharge reed valve is less susceptible to fatigue failure, and the compressor can exhibit high durability. The squeeze film effect is that when the parallel gap decreases at a speed V, the fluid is viscous and resists being pushed out of the gap, generating pressure (proportional to the viscosity coefficient and speed V). It is.

Under the above action, this compressor increases the pressure receiving area of the valve portion to increase the force for opening the discharge port, and reduces the over-compression by reducing the adhesion force of the lubricating oil that hinders valve opening. It becomes possible to suppress power loss.

Therefore, the compressor of the present invention can further reduce power loss and exhibit more excellent durability.

Further, in this compressor, since the discharge pulsation can be reduced by suppressing the delay in opening the discharge reed valve, the silence of the compressor can be improved. Furthermore, this compressor tends to reduce excitation force, bearing load, piston side force (lateral force), etc. due to reduction of overcompression, which can reduce mechanical loss and suppress wear. it can. As a result, it is possible to save power and improve reliability.

Note that Japanese Unexamined Patent Application Publication No. 2009-235913 discloses a compressor provided with a support portion that bisects the entire suction port. However, the present invention has a significant advantage over the technique disclosed in this document in that it has an excellent effect on the discharge side where more severe performance is required.

¡If the width of the support part, the main connecting part and the receiving part is large, fatigue failure of the valve part is unlikely to occur. On the other hand, if the areas of the support part, the main connection part and the receiving part are increased, the area of the discharge port is reduced, and the contact area of the support part, the main connection part and the receiving part is increased, resulting in an increase in the adhesion force. It is difficult to obtain the advantage of easy opening of the port. In order to solve these conflicting problems, the present invention can appropriately select the size and shape of the support portion, the main connection portion, and the receiving portion.

Preferably, the partition includes a sub-connecting portion extending from the support portion so as to at least bisect a base end discharge region of the discharge port located on the base end side in the longitudinal direction from the support portion. The discharge port is provided through the partition so as to leave the support portion, the receiving portion, the main connection portion, and the sub-connection portion.

In this case, the discharge port is divided into two or more divided ports by the support portion, the receiving portion, the main connection portion, and the sub-connection portion. In this case, the strength of the support portion is increased, and the valve portion that bends like a whip is easily supported sequentially from the proximal end side to the distal end side in the longitudinal direction, and fatigue failure of the valve portion can be effectively prevented.

Preferably, the sub-connecting portion extends along the longitudinal direction. The discharge port is divided into two divided ports by the sub-connecting portion, the support portion, the main connecting portion, and the receiving portion.

In this case, it is easy to realize the prevention of fatigue failure of the valve portion and the advantage that the discharge port is easily opened.

Preferably, the sub-connecting portion, the support portion, the main connecting portion, and the receiving portion have a width that widens toward the distal end side in the longitudinal direction.

In this case, it is possible to more easily open the discharge port in the proximal discharge region, and the receiving portion more suitably receives the distal end region of the valve portion, thereby further preventing fatigue failure of the valve portion.

Preferably, the sub-connecting portion includes a first sub-connecting portion extending along the longitudinal direction, a second sub-connecting portion extending along a direction that forms an angle of 90 ° clockwise with the main connecting portion, A main connecting portion and a third sub connecting portion extending in a direction that forms an angle of 90 ° counterclockwise. The discharge port is divided into four divided ports by the first sub-connection portion, the second sub-connection portion, the third sub-connection portion, the support portion, the main connection portion, and the receiving portion.

Also in this case, it is easy to realize the advantage of preventing the fatigue failure of the valve portion and the advantage that the discharge port is easily opened.

Preferably, the sub-connecting portion extends in a direction that forms a 120 ° clockwise angle with the main connecting portion, and a direction that forms an angle of 120 ° counterclockwise with the main connecting portion. And a second sub-connecting portion extending along the line. The discharge port is divided into three divided ports by the first sub-connecting portion, the second sub-connecting portion, the support portion, the main connecting portion, and the receiving portion.

Preferably, the sub-connection part, the support part, the main connection part, and the receiving part are flush with the fixed surface.

In this case, the processing cost can be suppressed.

Preferably, the sub-connection portion, the support portion, the main connection portion, and the receiving portion are formed with a recess that is recessed from the fixed surface.

In this case, the contact area between the valve portion of the discharge reed valve and the sub-connecting portion, the support portion, the main connecting portion, and the receiving portion is reduced, and the contact force is reduced and the valve is easily opened.

Preferably, the concave portion extends in a groove shape along the longitudinal direction.

In this case, the contact area is reduced, and the contact force due to the reverse squeeze effect is reduced when the valve is opened, so that the valve is easily opened.

Preferably, the concave portion extends in a groove shape along the width direction.

This will reduce the contact area. In addition, the amount of oil supplied from the fixed surface to the sub-connecting portion, the support portion, the main connecting portion, and the receiving portion is reduced, and the contact force is reduced, making it easier to open the valve.

Preferably, a crowning is formed in the sub-connecting portion, the support portion, the main connecting portion, and the receiving portion.

Also in this case, the contact area between the valve portion of the discharge reed valve and the sub-connecting portion, the support portion, the main connecting portion, and the receiving portion is reduced, and the contact force is reduced and the valve is easily opened.

Preferably, the valve portion extends in a direction different from the longitudinal direction with respect to the intermediate portion.

In this case, it is possible to easily increase the discharge port and increase the pressure receiving area of the valve portion. For this reason, it is possible to increase the force for opening the discharge port and to increase the contact force of the lubricating oil that prevents the valve opening at the intermediate portion. As a result, overcompression can be further reduced, and power loss can be reliably suppressed. Further, in this case, the tip region of the valve portion is more easily bent like a whip, and violently collides with the fixed surface. For this reason, the advantage of a support part, a main connection part, and a receiving part becomes more remarkable.

Preferably, the fixed surface includes a first groove portion extending so as to surround the discharge port, and a valve seat surface positioned between the discharge port and the first groove portion. The valve portion can contact the valve seat surface to close the discharge port. When the discharge reed valve in a state where the discharge port is closed is viewed in plan, the first groove portion extends to a range overlapping the intermediate portion.

In this case, the valve portion suitably seals the discharge port with the valve seat surface.

Preferably, the first groove is an annular groove surrounding the discharge port in the circumferential direction.

In this case, in a state where the discharge reed valve closes the discharge port, the intermediate portion and the arc portion facing the proximal end in the longitudinal direction in the annular groove overlap in a wider range. For this reason, the area where the fixing surface and the intermediate portion are in close contact with each other is reduced by the overlapping area.

Preferably, the first groove portion has a C shape that surrounds the discharge port in the circumferential direction except for a portion on the tip side in the longitudinal direction.

In this case, the receiving portion can be easily formed between them by widening the gap between the opposite ends on the front end side in the longitudinal direction of the C-shaped groove. For this reason, when the valve part of the discharge reed valve collides with the receiving part, the lubricating oil on the receiving part can surely relieve the collision force, so that only a small stress acts on the valve part, and the tip part of the valve part A large stress is unlikely to occur reliably. As a result, the compressor can effectively prevent the discharge reed valve from being damaged, and can reliably exhibit excellent durability.

Preferably, the fixing surface includes a second groove located on the proximal end side in the longitudinal direction with respect to the discharge port, and a communication groove located in a range overlapping with the intermediate portion and extending along the longitudinal direction. Have. When the discharge reed valve with the discharge port closed is viewed in plan, the second groove extends across the intermediate portion in the width direction. The communication groove communicates the first groove part and the second groove part.

The portion other than the communication groove on the fixed surface can be a contact portion that contacts the discharge reed valve.

In this case, when the discharge reed valve closes the discharge port, the second groove portion prevents foreign matter from being caught in the intermediate portion. In addition, when the discharge reed valve is opened, a mixed phase jet composed of gas and lubricating oil can blow off the lubricating oil interposed between the intermediate portion and the fixed surface to cut off the oil film. Further, the jet is discharged from the first groove portion to the outside in the width direction of the discharge reed valve through the communication groove and the second groove portion. Therefore, the lubricating oil accumulated in the first groove portion can be blown off, and the lubricating oil accumulated between the fixed surface and the intermediate portion and the lubricating oil accumulated in the second groove portion can also be blown off. Further, the area where the fixed surface and the intermediate portion are in close contact with each other is reduced by the communication groove. For this reason, this compressor can advance the timing which a fixed surface and an intermediate part leave | separate, and it becomes difficult to produce gas overcompression.

1 is a longitudinal sectional view of a compressor according to Embodiment 1 of the present invention. The principal part expanded sectional view which shows the state which the discharge reed valve opened the discharge port in the compressor of FIG. The top view which extracts and shows the valve plate and the discharge valve plate in which the some discharge reed valve was formed in the compressor of FIG. The principal part enlarged plan view which shows the state which the discharge reed valve closed the discharge port in the compressor of FIG. FIG. 5 is an enlarged cross-sectional view of a main part along the line ZZ in FIG. 4 showing a state in which the discharge reed valve closes the discharge port in the compressor of FIG. In the compressor of FIG. 1, (A) is a plan view of a discharge port, etc., (B) is a plan view of a discharge region, and (C) is a cross-sectional view of a support portion. The top view of discharge ports etc. in the compressor concerning Example 2 of the present invention. The top view of discharge ports etc. in the compressor concerning Example 3 of the present invention. The top view of discharge ports etc. in the compressor concerning Example 4 of the present invention. FIG. 10 is a cross-sectional view of a support portion corresponding to line AA in FIG. 6 in a compressor according to Embodiment 5 of the present invention. FIG. 7 is a cross-sectional view of a support portion corresponding to line BB in FIG. 6 in a compressor according to Embodiment 6 of the present invention. FIG. 9 is a cross-sectional view of a support portion corresponding to the line BB in FIG. 6 in a compressor according to Embodiment 7 of the present invention. FIG. 10 is a cross-sectional view of a support portion corresponding to line AA in FIG. 6 in a compressor according to Embodiment 8 of the present invention. FIG. 10 is a cross-sectional view of a support portion corresponding to line AA in FIG. 6 in a compressor according to Embodiment 9 of the present invention. Sectional drawing of the support part corresponded in the BB line of FIG. 6 in the compressor which concerns on Example 9 of this invention. In the compressor which concerns on Example 10 of this invention, the part of (A) is a top view, such as a discharge port, The part of (B) is sectional drawing of a support part. In the compressor which concerns on Example 11 of this invention, the principal part enlarged plan view which shows the state which the discharge reed valve closed the discharge port. FIG. 18 is an enlarged cross-sectional view of a main part along line YY in FIG. 17 showing a state in which the discharge reed valve closes the discharge port in the compressor of FIG. In the compressor which concerns on Example 12 of this invention, the principal part enlarged plan view which shows the state which the discharge reed valve closed the discharge port. In the compressor which concerns on Example 13 of this invention, the principal part enlarged plan view which shows the state which the discharge reed valve closed the discharge port. The principal part enlarged plan view which shows the state which the discharge reed valve closed the discharge port in the compressor which concerns on Example 14 of this invention. The principal part enlarged plan view which shows the state which the discharge reed valve closed the discharge port in the compressor which concerns on Example 15 of this invention. Sectional drawing for demonstrating the contact | adhesion force etc. which act on a discharge reed valve. The graph which shows the relationship between the time of a compressor, and a bore | bore internal pressure.

Embodiments 1 to 15 embodying the present invention will be described below with reference to the drawings.

Example 1
The compressor of the first embodiment is a variable capacity swash plate compressor. As shown in FIG. 1, the compressor includes a cylinder block 1 having a plurality of cylinder bores 1a. The plurality of cylinder bores 1a are concentrically arranged at equal angular intervals and extend in parallel to each other. The cylinder block 1 is sandwiched between a front housing 3 positioned at the front and a rear housing 5 positioned at the rear, and is fastened by a plurality of bolts 7 in this state. A crank chamber 9 is formed inside the cylinder block 1 and the front housing 3. The rear housing 5 is formed with a suction chamber 5a and a discharge chamber 5b.

A shaft hole 3 a is formed in the front housing 3, and a shaft hole 1 b is formed in the cylinder block 1. A drive shaft 11 is rotatably supported in the shaft holes 3a and 1b via a shaft seal device 9a and radial bearings 9b and 9c. A pulley (not shown) or an electromagnetic clutch (not shown) is provided on the drive shaft 11, and a belt (not shown) driven by a vehicle engine is wound around the pulley or the electromagnetic clutch.

In the crank chamber 9, a lug plate 13 is disposed when the drive shaft 11 is press-fitted, and a thrust bearing 15 is provided between the lug plate 13 and the front housing 3. The drive shaft 11 is inserted into a swash plate 17 disposed in the crank chamber 9 and supports the swash plate 17. The lug plate 13 and the swash plate 17 are connected by a link mechanism 19 that supports the swash plate 17 so that the tilt angle can be changed.

In each cylinder bore 1a, a piston 21 is housed so as to be able to reciprocate. A valve unit 23 is provided between the cylinder block 1 and the rear housing 5. As shown in FIG. 2 in an enlarged manner, the valve unit 23 includes a suction valve plate 25 that contacts the rear end surface of the cylinder block 1, a valve plate 27 that contacts the suction valve plate 25, and a valve plate 27. The discharge valve plate 29 is in contact with the discharge valve plate 29, and the retainer plate 31 is in contact with the discharge valve plate 29. The retainer plate 31 also serves as a gasket. The intake valve plate 25, the valve plate 27, the discharge valve plate 29, and the retainer plate 31 are stacked in this order to constitute the valve unit 23.

As shown in FIG. 1,

shoes

33a and 33b that are paired in the front and rear are provided between the swash plate 17 and each piston 21, and the swash plate 17 swings with each pair of

shoes

33a and 33b. It is converted into a reciprocating motion of each piston 21.

The crank chamber 9 and the suction chamber 5a are connected by an extraction passage 35a, and the crank chamber 9 and the discharge chamber 5b are connected by an air supply passage (not shown). A capacity control valve (not shown) is provided in the air supply passage. This capacity control valve is configured so that the opening degree of the air supply passage can be changed according to the suction pressure. A condenser is connected to the discharge chamber 5b by piping, the condenser is connected to the evaporator via an expansion valve by piping, and the evaporator is connected to the suction chamber 5a of the compressor by piping. Each compression chamber 24 is formed by the cylinder bore 1 a, the piston 21 and the valve unit 23.

The valve plate 27, the discharge valve plate 29, and the retainer plate 31 are formed with a plurality of suction ports 23 a that allow the suction chamber 5 a to communicate with the compression chambers 24. The intake valve plate 25 is formed with a plurality of intake reed valves 25a for opening and closing each intake port 23a.

As shown in FIGS. 2 to 5, the suction valve plate 25 and the valve plate 27 are formed with a plurality of discharge ports 23b for communicating the compression chambers 24 with the discharge chambers 5b.

As shown in the part (A) of FIG. 6, each discharge port 23b has two divided ports 231 with respect to each cylinder bore 1a by a support part 27t, a receiving part 27h, a main connection part 27v, and a sub-connection part 27w described later. It is divided into 232.

As shown in FIG. 2, the discharge valve plate 29 is formed with a plurality of discharge reed valves 29a for opening and closing the divided

ports

231 and 232. The retainer plate 31 is formed with a retainer 31a that regulates the lift length of each discharge reed valve 29a. In the present embodiment, as shown in FIG. 3, the discharge valve plate 29 includes a circular portion and a plurality of (six in this embodiment) extending portions that extend radially outward from the circular portion. Each extending portion forms a discharge reed valve 29a that opens and closes each discharge port 23b.

As shown in FIGS. 4 to 6, an annular ring groove 27a surrounding the discharge port 23b in the circumferential direction is formed on the fixed surface 27f, which is the surface of the valve plate 27 facing the discharge chamber 5b. The annular groove 27a is an example of the first groove portion of the present invention. In the fixed surface 27f, an annular region sandwiched between the discharge port 23b and the annular groove 27a becomes a valve seat surface (also referred to as an eyeglass portion) 27b flush with the portion of the fixed surface 27f outside the annular groove 27a. ing. In this compressor, the suction valve plate 25 and the valve plate 27 are partition walls.

As shown in FIGS. 2 to 5, each of the six discharge reed valves 29a has a proximal end and a distal end, and is positioned at the proximal end and fixed to a fixing surface 27f of the valve plate 27. An intermediate portion 292a extending from the fixed portion 291a toward the tip along the longitudinal direction of the discharge reed valve 29a and capable of lifting, and a corresponding discharge port 23b extending from the intermediate portion 292a toward the tip along the longitudinal direction. And a valve portion 293a that opens and closes. In the present embodiment, the longitudinal direction is a direction parallel to the fixed surface 27 f and extending along the radial direction of the drive shaft 11. In particular, in FIG. 4, the longitudinal direction from the proximal end to the distal end of each discharge reed valve 29a is indicated by reference symbol D1, and the longitudinal direction from the distal end to the proximal end of each discharge reed valve 29a is indicated by reference symbol D2.

As shown in FIG. 4, when the intermediate part 292a and the valve part 293a are viewed in a plan view, the intermediate part 292a has a rectangular shape whose long side extends toward the distal end side along the longitudinal direction D1. The valve portion 293a has a short side of the intermediate portion 292a as a diameter, and has a circular shape concentric with the annular groove 27a. The diameter of the valve portion 293a in the direction orthogonal to the longitudinal direction D1 is larger than the diameter along the longitudinal direction D1 of the valve seat surface 27b.

4 and 6, the valve plate 27 includes a support portion 27t that receives the central region of the valve portion 293a, a receiving portion 27h that receives the tip region of the valve portion 293a, and a support portion 27t and a receiving portion 27h. A main connecting portion 27v to be connected and a sub connecting portion 27w extending from the support portion 27t are provided. The central region of the valve portion 293a is a certain range including the center since the valve portion 293a is circular. The tip region of the valve portion 293a is a certain range located on the tip side from the central region. As shown in the part (B) of FIG. 6, the valve plate 27 is provided with a discharge region A through which the discharge port 23 b is provided. The discharge area A includes a semicircular tip discharge area A1 located on the distal end side in the longitudinal direction D1, and a semicircular proximal discharge area A2 located on the proximal end side in the longitudinal direction D1. As shown in the part (A) of FIG. 6, the support portion 27 t is a certain range including the center O of the ejection region A. The support portion 27t is positioned so as to receive the central region of the valve portion 293a, and discharge ports 23b are present on the left and right of the distal end side and the left and right of the proximal end side in the longitudinal direction D1 when viewed from the support portion 27t. The main connecting portion 27v extends from the support portion 27t so as to bisect the tip discharge region A1. The sub-linking part 27w bisects the proximal discharge area A2. The valve plate 27 is provided with a discharge port 23b so as to leave a support portion 27t, a receiving portion 27h, a main connection portion 27v, and a sub-connection portion 27w. Since the valve plate 27 is provided with the support portion 27t, the receiving portion 27h, the main connecting portion 27v, and the sub connecting portion 27w, the discharge port 23b is divided into two divided

ports

231 and 232.

The sub-connecting portion 27w, the support portion 27t, the main connecting portion 27v, and the receiving portion 27h have an I-shape that extends toward the distal end side in the longitudinal direction D1. As shown in the part (C) of FIG. 6, the support portion 27t, the receiving portion 27h, the main connection portion 27v, and the sub-connection portion 27w are flush with the fixed surface 27f. Between the divided

ports

231 and 232, a support portion 27t, a receiving portion 27h, a main connection portion 27v, and a sub connection portion 27w exist. The divided

ports

231 and 232 having such a shape are formed by punching and pressing the valve plate 27, for example.

As shown in the part (A) of FIG. 6, the widths of the support portion 27t, the main connection portion 27v, and the sub-connection portion 27w are equal in the direction orthogonal to the longitudinal direction D1, but the width of the receiving portion 27h is the support portion 27t, It is formed larger than the width of the main connecting portion 27v and the sub connecting portion 27w. Note that the corners of the divided

ports

231 and 232 are slightly rounded, not pin angles, due to processing accuracy limitations such as punching press processing.

As shown in FIGS. 2 to 5, the fixed surface 27f is formed with a long groove 27c that is located on the proximal end side in the longitudinal direction D1 with respect to the discharge port 23b and extends across the intermediate portion 292a in the width direction. . The long groove 27c is an example of the second groove portion of the present invention. As shown in FIG. 4, when the long groove 27c is viewed in plan, the shape of the long groove 27c is an elongated oval shape orthogonal to the longitudinal direction D1. The long groove 27c is formed deeper than the annular groove 27a.

In the compressor configured as described above, when the drive shaft 11 is rotationally driven, the lug plate 13 and the swash plate 17 rotate synchronously with the drive shaft 11, and each stroke is performed according to the inclination angle of the swash plate 17. The piston 21 reciprocates in each cylinder bore 1a. For this reason, the refrigerant gas in the suction chamber 5a is sucked into each compression chamber 24, compressed, and discharged into the discharge chamber 5b. The refrigerant gas that is compressed by the compressor contains mist-like lubricating oil. This lubricating oil is interposed in sliding portions such as the pistons 21, the

shoes

33a and 33b, the swash plate 17, and the like to suppress wear. Lubricating oil also accumulates in the annular groove 27a and the long groove 27c.

During this time, as shown in FIG. 2, due to the difference between the pressure in the discharge chamber 5b and the pressure in the compression chamber 24, the discharge reed valve 29a is elastically deformed by the intermediate portion 292a and the discharge port 23b is opened by the valve portion 293a. As shown in FIG. 5, the valve portion 293a does not open the discharge port 23b until the pressure difference overcomes the contact force of the intermediate portion 292a.

In this compressor, even when the discharge reed valve 29a is closed, the central region of the valve portion 293a is supported by the support portion 27t even if the central region of the valve portion 293a tends to be greatly bent into the discharge port 23b due to inertia force or pressure difference. The Further, since the sub-connecting portion 27w, the supporting portion 27t, the main connecting portion 27v, and the receiving portion 27h are formed in an I shape extending along the longitudinal direction D1, the strength of the supporting portion 27t is increased and the longitudinal direction D1 is increased. The valve portion 293a that collides with the fixed surface 27f while being bent like a whip along the distal end side along the distal direction is easily and preferably supported sequentially from the proximal end side in the longitudinal direction D1 toward the distal end side. For this reason, it is hard to produce fatigue failure in the valve part 293a.

In particular, in this compressor, when the valve portion 293a of the discharge reed valve 29a collides with the receiving portion 27h, the lubricating oil on the receiving portion 27h relaxes the collision force by the squeeze film effect, and only a small stress acts on the valve portion 293a. Therefore, it is difficult for large stress to be generated at the tip of the valve portion 293a. For this reason, the discharge reed valve 29a is less susceptible to fatigue failure, and the compressor can exhibit high durability.

In this compressor, under the above-described action, the pressure receiving area of the valve portion 293a is increased to increase the force for opening the discharge port 23b, and by reducing the contact force of the lubricating oil that hinders the valve opening, It becomes possible to reduce, and it becomes possible to suppress power loss.

Therefore, this compressor can further reduce power loss and exhibit superior durability.

In this compressor, since the discharge pulsation can be reduced by suppressing the delay in opening of the discharge reed valve 29a, the quietness of the compressor can be improved. Further, in this compressor, the peak pressure in the compression chamber 24 can be reduced, so that the maximum compression load is reduced, the contact surface between the thrust bearing 15, the

shoes

33a, 33b and the piston 21, the

shoes

33a, 33b, and the swash plate 17. This increases the reliability of the sliding surface.

Further, in this compressor, as shown in FIG. 4, an annular groove 27a is formed on the fixed surface 27f. Therefore, in a state where the discharge reed valve 29a closes the discharge port 23b, the intermediate portion 292a and the circular arc portion 27g (shown in FIG. 4) of the annular groove 27a overlap in a wide range. For this reason, the area where the fixing surface 27f and the intermediate portion 292a are in close contact with each other is reduced by the overlapping area. For this reason, the opening delay of the discharge reed valve 29a can be reduced.

Furthermore, in this compressor, a long groove 27c is formed in the fixed surface 27f. For this reason, in a state where the discharge reed valve 29a closes the discharge port 23b, foreign matter is prevented from being caught in the intermediate portion 292a.

(Example 2)
In the compressor of the second embodiment, as shown in FIG. 7, the discharge port 23b is configured by combining four fan-shaped divided ports 231 to 234 having a central angle of about 90 degrees.

The valve plate 27 includes a support portion 27d, a main connection portion 27v, a receiving portion 27h, and first to third sub-connection portions 27w1 to 27w3. The first sub coupling portion 27w1 extends along the longitudinal direction D1. The second sub-connecting portion 27w2 extends along a direction that forms a 90 ° clockwise angle with the main connecting portion 27v. The third sub-connecting portion 27w3 extends along a direction that forms an angle of 90 ° counterclockwise with the main connecting portion 27v. Between the divided ports 231 to 234, there are a support portion 27d, a main connection portion 27v, a receiving portion 27h, and first to third sub-connection portions 27w1 to 27w3. Other configurations are the same as those of the compressor of the first embodiment.

This compressor can provide the same advantages as the compressor of the first embodiment.

(Example 3)
As shown in FIG. 8, in the compressor of the third embodiment, the discharge port 23b is configured by combining three fan-shaped divided ports 231 to 233 having a central angle of about 120 degrees.

The valve plate 27 is formed with a support portion 27e, a main connection portion 27v, a receiving portion 27h, and first and second sub-connection portions 27w1 and 27w2. The first sub-connecting portion 27w1 extends along a direction that forms an angle of 120 ° clockwise with the main connecting portion 27v. The second sub-connecting portion 27w2 extends along a direction that forms an angle of 120 ° counterclockwise with the main connecting portion 27v. Between the divided ports 231 to 233, there are a support portion 27e, a main connection portion 27v, a receiving portion 27h, and first and second sub-connection portions 27w1 and 27w2. Other configurations are the same as those of the compressor of the first embodiment.

Example 4
As shown in FIG. 9, the compressor of the fourth embodiment has half-moon shaped divided

ports

231 and 232. Further, the sub-connecting portion 27w, the support portion 27i, the main connecting portion 27v, and the receiving portion 27j have a width that widens toward the distal end side in the longitudinal direction D1. Other configurations are the same as those of the compressor of the first embodiment.

According to the present invention, the large deflection of the central region of the valve portion 293a into the discharge port 23b can be greatly reduced. For this reason, the valve part 293a does not necessarily need to contact over the whole support part, receiving part, main connection part, and sub-connection part. For this reason, the following embodiments 5 to 10 may be employed.

(Example 5)
In the compressor according to the fifth embodiment, as shown in FIG. 10, a recess 27k is formed on the surface of the support portion 27t or the like. The recess 27k is formed in a groove shape at both ends in the width direction such as the support portion 27t. Other configurations are the same as those of the compressor of the first embodiment.

In this compressor, the contact area between the valve portion 293a and the support portion 27t is reduced, the contact force is reduced, and the valve is easily opened. Further, with this structure, it is possible to suppress the contact area and hence the adhesion force while maintaining the strength by giving the support portion 27t a width. Other advantages are the same as those of the first embodiment.

(Example 6)
In the compressor according to the sixth embodiment, as shown in FIG. 11, a recess 28a is formed on the surface of the support portion 27t and the like. The concave portion 28a is formed in a groove shape along the longitudinal direction of the support portion 27t and the like. Other configurations are the same as those of the compressor of the first embodiment.

In this compressor, the contact area is reduced, and the close contact force due to the reverse squeeze effect is reduced when the valve is opened, so that the valve is easily opened. Other advantages are the same as those of the first embodiment.

(Example 7)
In the compressor of the seventh embodiment, as shown in FIG. 12, narrow groove-shaped recesses 27m are formed at both ends in the length direction of the support portion 27t and the like. The concave portion 27m extends along the width direction of the support portion 27t and the like. Other configurations are the same as those of the compressor of the first embodiment.

In this compressor, since the recess 27m cuts off the lubricant oil between the valve seat surface 27b and the support portion 27t, the supply of the lubricant oil from the valve seat surface 27b to the support portion 27t is cut off. The contact force acting between the support portion 27t and the like and the valve portion 293a is reduced, and the valve is easily opened. Other advantages are the same as those of the first embodiment.

(Example 8)
In the compressor of Example 8, as shown in FIG. 13, together with the concave portions 27s at both ends, three thin groove-shaped concave portions 27n positioned between them are formed in the support portion 27t and the like. Other configurations are the same as those of the compressor of the sixth embodiment.

In this compressor, the contact area between the support part 27t and the like and the valve part 293a is reduced, the contact force is reduced, and the valve is easily opened. Other advantages are the same as those of the first embodiment.

Example 9
In the compressor of the ninth embodiment, as shown in FIG. 14 or FIG. 15, a crowning 27p is formed on the support portion 27t and the like. Other configurations are the same as those of the compressor of the first embodiment.

Also in this compressor, the contact area between the valve portion 293a and the support portion 27t is reduced, the contact force is reduced, and the valve is easily opened. Other advantages are the same as those of the first embodiment.

(Example 10)
In the compressor of the tenth embodiment, as shown in FIG. 16, a plurality of recesses 27q are formed by performing coining on the support portion 27t and the like and then grinding. Other configurations are the same as those of the compressor of the first embodiment. This compressor can also provide the same advantages as the compressor of the sixth embodiment.

(Example 11)
In the compressor of the eleventh embodiment, as shown in FIGS. 17 and 18, a communication groove 27r extending toward the distal end side in the longitudinal direction D1 and communicating the annular groove 27a and the long groove 27c is formed on the fixed surface 27f. Yes. A portion of the fixed surface 27f other than the communication groove 27r serves as a contact portion 27s that contacts the discharge reed valve 29a. The contact portion 27s is positioned on both sides in the width direction of the communication groove 27r on the fixed surface 27f, and overlaps the intermediate portion 292a when the discharge reed valve 29a with the discharge port 23b closed is viewed in plan view. In this embodiment, the width of the communication groove 27r is about 50% to 75% with respect to the width of the intermediate portion 292a, and the contact portion 27s can reliably support the intermediate portion 292a.

In this compressor, when the discharge reed valve 29a is opened, a mixed phase jet composed of refrigerant gas and lubricating oil can blow off the lubricating oil interposed between the intermediate portion 292a and the fixed surface 27f to cut off the oil film. Further, since the jet is discharged from the annular groove 27a to the outside in the width direction of the discharge reed valve 29a through the communication groove 27r and the long groove 27c, the lubricating oil accumulated in the annular groove 27a can be blown off, and the fixed surface 27f The lubricating oil collected between the intermediate portion 292a and the lubricating oil collected in the long groove 27c can also be blown away. Further, the area where the fixing surface 27f and the intermediate portion 292a are in close contact with each other is reduced by the communication groove 27r. For this reason, this compressor can advance the timing which the fixed surface 27f and the intermediate part 292a space apart, and it becomes difficult to produce overcompression of refrigerant gas. Other advantages are the same as those of the first embodiment.

(Example 12)
In the compressor of the twelfth embodiment, as shown in FIG. 19, the valve portion 293a has a circular shape having a diameter equal to or larger than the short side of the intermediate portion 292a. That is, the valve portion 293a extends in a direction different from the longitudinal direction D1 with respect to the intermediate portion 292a. Other configurations are the same as those of the first embodiment.

In this case, it is possible to easily increase the discharge port 23b and increase the pressure receiving area of the valve portion 293a. For this reason, it is possible to increase the force for opening the discharge port 23b and to avoid an increase in the adhesion force of the lubricating oil that prevents the valve opening at the intermediate portion 292a. As a result, overcompression can be further reduced, and power loss can be reliably suppressed. In this case, the tip of the valve portion 293a toward the tip in the longitudinal direction D1 is more likely to be bent like a whip, and violently collides with the fixed surface 27f. For this reason, the advantages of the support portion 27t and the like become more prominent. Other advantages are the same as those of the first embodiment.

(Example 13)
In the compressor of Example 13, as shown in FIG. 20, instead of the support part 27t of Example 1, the support part 27i of Example 4 is adopted, and instead of the annular groove 27a of Example 1, A C-shaped groove 27c is employed. The C-shaped groove 27c is also an example of the first groove portion of the present invention. The C-shaped groove 27c is formed in an arc shape concentric with the center O on the fixed surface 27f, and surrounds the discharge port 23b in the circumferential direction except for the distal end side in the longitudinal direction D1. The region of the fixed surface 27f sandwiched between the opposite ends of the C-shaped groove 27y is a receiving portion 27z together with the receiving portion 27j. Other configurations are the same as those of the first embodiment.

In this case, by widening the gap between the opposite ends of the C-shaped groove 27y, the other portion of the support portion 27i (the portion of the support portion 27i other than the receiving

portions

27j and 27z) is interposed between them. The receiving

portions

27j and 27z formed large in the width direction can be easily formed. For this reason, when the valve portion 293a collides with the receiving

portions

27j, 27z, the lubricating oil on the

large receiving portions

27j, 27z can reliably relieve the collision force, so that only a small stress acts on the valve portion 293a, and the valve It is difficult for a large stress to occur reliably at the tip of the portion 293a. As a result, the compressor can effectively prevent the discharge reed valve 29a from being damaged, and can reliably exhibit excellent durability. Other advantages are the same as those of the first embodiment.

(Example 14)
In the compressor of Example 14, as shown in FIG. 21, instead of the support part 27t of Example 1, the support part 27i of Example 4 is adopted, and instead of the annular groove 27a of Example 1, A pair of first groove portions 27x is employed. Both the first groove portions 27x are formed in an arc shape concentric with the center O on the fixed surface 27f, and surround the discharge port 23b from the left and right except for the distal end side and the proximal end side in the longitudinal direction D1. In the fixed surface 27f, a region sandwiched between ends facing each other on the distal end side in the longitudinal direction D1 in both first groove portions 27x is a receiving portion 27z together with the receiving portion 27j. On the other hand, in the fixed surface 27f, a region sandwiched between ends facing each other on the base end side in the longitudinal direction D1 in both first groove portions 27x is a base end side receiving portion 274. Other configurations are the same as those of the first embodiment.

In this case, the receiving

portions

27j and 27z larger than the other portions can be easily formed between the first groove portions 27x by widening the distance between the opposing ends on the leading end side in the longitudinal direction D1. For this reason, similarly to the compressor of the thirteenth embodiment, it is difficult to reliably generate a large stress at the tip of the valve portion 293a. Further, in this compressor, when the intermediate portion 292a of the discharge reed valve 29a collides with the proximal end side receiving portion 274, only a small stress acts on the intermediate portion 292a by the large proximal end receiving portion 274. As a result, the compressor can effectively prevent the discharge reed valve 29a from being damaged, and can reliably exhibit excellent durability. Other advantages are the same as those of the first embodiment.

(Example 15)
In the compressor of the fifteenth embodiment, as shown in FIG. 22, the valve plate 27 is provided with only the support portion 27u, the main coupling portion 27v, and the receiving portion 27h, and the U-shaped discharge port 23b is employed. For this reason, the support part 27u can receive the center area | region of the valve part 293a similarly to the support part 27t of Example 1. FIG. Other configurations are the same as those of the first embodiment.

In this case, the same advantages as in the first embodiment can be obtained.

In the above, the present invention has been described with reference to the first to fifteenth embodiments. However, the present invention is not limited to the first to fifteenth embodiments, and can be appropriately modified and applied without departing from the spirit of the present invention. Needless to say.

For example, the support portion or the like may be formed on the valve plate 27 itself, or may be formed on a member other than the valve plate 27, which is a member such as a damping steel plate.

In the first embodiment, the long groove 27c is formed deeper than the annular groove 27a. In the eleventh embodiment, the annular groove 27a, the long groove 27c, and the communication groove 27r are formed at the same depth. However, these depths are not limited thereto. It is not something.

The

concave portions

27k, 27a, 27m, 27s, 27q and the crowning 27p described in the fifth to tenth embodiments may be provided only in the support portion 27t, or the support portion 27t, the main connection portion 27v, and the sub-connection portions 27w, 27w1 to It may be provided across 27w3.

The present invention can be used for a vehicle air conditioner.

Claims

A discharge chamber;
A compression chamber;
A partition provided between the discharge chamber and the compression chamber and having a fixed surface facing the discharge chamber, the partition having a discharge port capable of communicating the discharge chamber and the compression chamber;
A discharge reed valve having a length extending along the longitudinal direction, a distal end, and a proximal end, the discharge reed valve being positioned at the proximal end and fixed to the fixed surface; An intermediate portion extending from the fixed portion toward the tip and capable of being lifted with respect to the fixed surface; and a valve portion further extending from the intermediate portion toward the tip and capable of opening and closing the discharge port. A discharge reed valve;
With
The partition wall bisects a support portion that supports a central region of the valve portion, a receiving portion that receives a tip region of the valve portion, and a tip discharge region of a discharge port located on the tip side in the longitudinal direction from the support portion. And a main coupling part extending from the support part and coupling the support part and the receiving part,
In the partition wall, the discharge port is provided so as to leave the support portion, the receiving portion, and the main coupling portion,
The compressor has a width that is greater than a width of the support portion in a direction orthogonal to the longitudinal direction.
The partition includes a sub-connecting portion extending from the support portion so as to at least bisect a base end discharge region of a discharge port located on the base end side in the longitudinal direction from the support portion,
2. The compressor according to claim 1, wherein the discharge port is provided in the partition so as to leave the support portion, the receiving portion, the main connection portion, and the sub-connection portion.
The sub-connecting portion extends along the longitudinal direction,
The compressor according to claim 2, wherein the discharge port is divided into two divided ports by the sub-connecting portion, the support portion, the main connecting portion, and the receiving portion.
The compressor according to claim 3, wherein the sub-connecting portion, the support portion, the main connecting portion, and the receiving portion have a width that widens toward the distal end side in the longitudinal direction.
The sub-connecting portion includes a first sub-connecting portion extending along the longitudinal direction, a second sub-connecting portion extending along a direction that forms a 90 ° clockwise angle with the main connecting portion, and the main connecting portion. And a third sub-connecting portion extending along a direction that forms an angle of 90 ° counterclockwise,
The discharge port is divided into four divided ports by the first sub-connecting portion, the second sub-connecting portion, the third sub-connecting portion, the support portion, the main connecting portion, and the receiving portion. Item 3. The compressor according to Item 2.
The sub-connecting portion extends along a direction that forms an angle of 120 ° clockwise with the main connecting portion, and a direction that forms an angle of 120 ° with the main connecting portion counterclockwise. A second sub-connecting portion extending,
The compressor according to claim 2, wherein the discharge port is divided into three divided ports by the first sub-connecting portion, the second sub-connecting portion, the support portion, the main connecting portion, and the receiving portion. .
The compressor according to claim 2, wherein the sub-connecting portion, the support portion, the main connecting portion, and the receiving portion are flush with the fixed surface.
The compressor according to claim 2, wherein the sub-connection portion, the support portion, the main connection portion, and the receiving portion are formed with a recess that is recessed from the fixed surface.
The compressor according to claim 8, wherein the recess extends in a groove shape along the longitudinal direction.
The compressor according to claim 8, wherein the recess extends in a groove shape along the width direction.
The compressor according to claim 2, wherein a crowning is formed in the sub-connecting portion, the support portion, the main connecting portion, and the receiving portion.
The compressor according to any one of claims 1 to 11, wherein the valve portion extends in a direction different from the longitudinal direction with respect to the intermediate portion.
The fixed surface includes a first groove portion extending so as to surround the discharge port, and a valve seat surface positioned between the discharge port and the first groove portion, and the valve portion is configured to close the discharge port. The first groove portion extends to a range overlapping the intermediate portion when the discharge reed valve in a state of being able to contact the valve seat surface and having the discharge port closed is viewed in a plan view. The compressor according to any one of the above.
The compressor according to claim 13, wherein the first groove is an annular groove surrounding the discharge port in the circumferential direction.
The compressor according to claim 13, wherein the first groove portion has a C shape surrounding the discharge port in a circumferential direction except for a portion on the tip side in the longitudinal direction.
The fixed surface has a second groove located on the proximal end side in the longitudinal direction with respect to the discharge port, and a communication groove located in a range overlapping with the intermediate portion and extending along the longitudinal direction, When the discharge reed valve with the discharge port closed is viewed in plan, the second groove extends across the intermediate portion in the width direction, and the communication groove communicates the first groove portion and the second groove portion. The compressor according to any one of claims 13 to 15.