JP2002202052A - Variable displacement compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a variable displacement compressor easily obtainable by a brief manufacturing method, and capable of reducing a cost. SOLUTION: In this variable displacement compressor interposing a hinge mechanism 20 between a rotary support 17 and a cam plate 18, and constituted so as to control delivery displacement by changing a stroke of a piston 23 by changing an inclination of the cam plate 18 between a maximum inclination and a minimum inclination by a guide of the hinge mechanism 20, the cam plate 18 is composed of a disk member and a mooring member for constituting a hinge part 20, both of these parts are formed by press molding, and these are joined and fixed by welding or rivets.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a variable displacement compressor applied to, for example, a vehicle air conditioning system.

[0002]

2. Description of the Related Art As a conventional compressor of this type, a compressor as disclosed in Japanese Patent Application Laid-Open No. 10-274153 is known. This prior art is configured as shown in FIGS. 6 and 7. That is, the rotary support 101 is fixed on the drive shaft 102. Cam plate 103
Is provided with an insertion hole 103a at the center thereof.
The drive shaft 102 is inserted through 03a with a predetermined clearance. The piston 104 includes a housing 105
The cam plate 103 is housed in a cylinder bore 105a provided on the cam plate 103, and is moored through a shoe 106 to an outer peripheral portion of the cam plate 103.

[0003] The hinge mechanism 107 is interposed between the rotary support 101 and the cam plate 103. The hinge mechanism 107 includes a guide pin 108 provided on the cam plate 103, and a support arm 109 provided on the rotary support 101 corresponding to the guide pin 108. The spherical portion 108a is provided at the tip of the guide pin 108. The guide hole 109a is provided in the support arm 109. The guide hole 109a extends so as to approach the axis of the drive shaft 102 from outside. The guide pin 108 is inserted into the guide hole 109a of the support arm 109 with the spherical portion 108a.

The cam plate 103 is driven by a driving shaft 102 via a rotating support 101 and a hinge mechanism 107.
And can rotate together. Therefore, the cam plate 103
Is converted into a linear reciprocating motion of the piston 104 via the shoe 106, and a series of compression cycles of suction, compression and discharge of the refrigerant gas in the cylinder bore 105a are performed. As shown in FIG.
There to correspond to the piston 104 drives out the top dead center position D _1, the piston 104 is located at the top dead center. The cam plate 103 is rotated 180 ° from the drawing state, corresponding to the piston 104 drives out the bottom dead center position D _2, the piston 104 is positioned at the bottom dead center.

The cam plate 103 includes a hinge mechanism 1
By the guidance of 07, it is possible to incline while sliding on the drive shaft 102 between a maximum inclination position where the inclination angle is maximized shown in FIG. 6 and a minimum inclination position (not shown) where the inclination angle is minimized. is there. When the inclination angle of the cam plate 103 is changed, the position of the bottom dead center is changed while the position of the top dead center of the piston 104 remains unchanged. As a result, the stroke of the piston 104 is changed, and the displacement is adjusted.

Further, the cam plate 103 is provided with a maximum tilt angle defining portion 103b on the side opposite to the guide pin 108 with respect to the insertion hole 103a. When the cam plate 103 is at the maximum tilt position, the maximum tilt defining portion 103b comes into contact with the receiving portion 101a of the rotary support 101.

[0007]

Here, conventionally, the cam plate 103 has been obtained by machining (cutting) a cast material. That is, as shown in FIG. 7, a material integrally including a mooring portion including the thick portion 103d, the maximum inclination defining portion 103b, and the guide pin holding portion 103e and the disk portion 103c is formed by casting, and is machined. After that, the separately formed guide pin 108 was fitted to obtain the desired cam plate 103. The portions to be machined include the flat surface and the circumferential surface of the disk portion 103c, the upper end surface of the guide pin holding portion of the mooring portion, the insertion hole of the guide pin 108, the end surface of the maximum tilt angle defining portion, and the insertion hole 103a. Etc.

However, in the above-described conventional manufacturing method, since the cam plate 103 is formed integrally by casting, the size of the cam plate 103 is increased and the weight is increased due to excess wall thickness. In addition, there is a problem that after the molding by casting, many places need to be cut, and it takes time to process the cam plate.

SUMMARY OF THE INVENTION The present invention has been made in view of the problems existing in the prior art described above, and has as its object to simplify the cam plate by using press molding for forming the components of the cam plate. It is an object of the present invention to provide a variable displacement compressor which can form a compressor.

[0010]

According to the first aspect of the present invention, a cylinder bore and a crank chamber are formed in a housing, a drive shaft is supported, a piston is accommodated in the cylinder bore, and a crank is provided. A rotary support is fixed to the drive shaft in the room, and a cam plate is similarly supported on the drive shaft in a tiltable manner in the crank chamber, and a hinge mechanism is interposed between the rotary support and the cam plate. In the variable displacement compressor in which the discharge capacity can be changed by sliding the cam plate while being inclined in the axial direction of the drive shaft by the guide of the mechanism,
The cam plate is composed of two or more members including a mooring member constituting a hinge mechanism and a disk member connected to the piston, and at least one member is formed by press molding. Abstract. According to the present invention, the constituent members of the cam plate can be easily processed by press molding.

According to a second aspect of the present invention, in the first aspect of the present invention, the cam plate is formed by joining and fixing two members of a mooring member and a disk member. According to the present invention, the cam plate is composed of two members, the mooring member and the disk member.

According to a third aspect of the present invention, in the first or second aspect, the disk member is formed by press forming. According to the present invention, the disk member can be easily processed by press working.

According to a fourth aspect of the present invention, in the first to third aspects, the mooring member is formed by press molding. According to the present invention, the mooring member can be easily processed by press working.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment in which the present invention is embodied in a single-head piston type variable displacement compressor applied to a vehicle air conditioning system will be described below.

As shown in FIG. 1, the front housing 1
1 is a cylinder block 12 as a center housing
Is fixedly attached to the front end. The rear housing 13
The rear end of the cylinder block 12 is joined and fixed via a valve forming body 14. The front housing 11, the cylinder block 12, and the rear housing 13 constitute a compressor housing. The crank chamber 15 is defined by being surrounded by the front housing 11 and the cylinder block 12. The drive shaft 16 is rotatably supported between the front housing 11 and the cylinder block 12 so as to pass through the crank chamber 15. The drive shaft 16 is
It is connected to a vehicle engine as an external drive source (not shown) via a clutch mechanism such as an electromagnetic clutch. Therefore, the drive shaft 16 is rotationally driven by the connection of the electromagnetic clutch when the vehicle engine is started.

The rotary support 17 is fixed to the drive shaft 16 in the crank chamber 15. The cam plate 18 is housed in the crank chamber 15. The drive shaft 16 is inserted through an insertion hole 19 formed through the center of the cam plate 18. The hinge mechanism 20 is interposed between the rotation support 17 and the cam plate 18.

The cam plate 18 is shown in FIGS.
It will be described in further detail based on The cam plate 18 is shown in FIG.
And the hinge mechanism 20 shown in FIG.
Is fixedly joined to the mooring member 18b by welding (for example, spot welding, projection welding, or the like) or by rivets or the like, and has a configuration as shown in FIG. Here, as shown in FIG. 3, the disc member 18a has a disc shape and a hole 19a serving as an insertion hole 19 is formed in the center. For example, a rolled steel plate can be formed by punching a press. Further, as shown in FIG. 4, the mooring member 18b is obtained, for example, by pressing a rolled steel plate into a U-shape. At this time, the mooring piece 18c is formed at one end of the bent piece press-formed in a U-shape, and the maximum inclination defining portion 32 is formed at the other end.
As shown in FIG. 1, a pin hole 18d for inserting the hinge pin 21 is formed at the tip of each of the mooring pieces 18c. A hole 19b serving as an insertion hole 19 is formed in the center of the base of the mooring member 18b.

As shown in FIG. 1, at the position corresponding to the mooring piece 18c, a support arm 33 constituting the hinge mechanism 20 is projected from the rotary support 17, and its tip is divided into two branches. The tip of the mooring piece 18c is inserted into 33a. The guide hole 3 is formed in the forked portion 33a.
3b is formed, and the hinge pin 21 is inserted into the guide hole 33b and can be guided and moved. As a result, the cam plate 18 has the maximum tilt angle defining portion 32
Is slidable between a maximum tilt position where the disc portion 18a of the cam plate 18 contacts the circlip 31 and a maximum tilt position where the disc portion 18a of the cam plate 18 contacts the circlip 31. A compression spring 22 is interposed between the rotation support 17 and the cam plate 18 through the drive shaft 16.

A plurality of cylinder bores 12a are formed at predetermined intervals around a drive shaft 16 (axis L) in the cylinder block 12 (only one is shown in the drawing). The single-headed piston 23 is housed in each cylinder bore 12a. The piston 23 is connected to the disc member 1 via the shoe 24.
8a is moored around the outer periphery.

The suction chamber 25 is defined at the center of the rear housing 13. The discharge chamber 26 is defined on the outer periphery of the rear housing 13. Suction port 27,
The suction valve 28, the discharge port 29, and the discharge valve 30 are formed on the valve forming body 14, respectively.

The cam plate 18 includes a rotating support 17.
And can be integrally rotated with the drive shaft 16 via the hinge mechanism 20. Cam plate 18 accompanying rotation of drive shaft 16
Swinging back and forth in the direction of the axis L is converted into reciprocating motion of the piston 23 via the shoe 24.

The refrigerant gas in the suction chamber 25 moves from the top dead center side of the piston 23 to the bottom dead center side, thereby causing the suction port 27 to move.
And, it is sucked into the cylinder bore 12a through the suction valve 28. The refrigerant gas sucked into the cylinder bore 12a is compressed by moving from the bottom dead center side of the piston 23 to the top dead center side, and is discharged to the discharge chamber 26 via the discharge port 29 and the discharge valve 30.

The bleed passage 35 includes the crank chamber 15 and the suction chamber 2.
5 is communicated. The air supply passage 36 connects the discharge chamber 26 and the crank chamber 15. The capacity control valve 37 is interposed on the air supply passage 36. The pressure-sensitive passage 38 communicates the suction chamber 25 with the displacement control valve 37. The displacement control valve 37 is a pressure-sensitive valve, and the displacement control valve 37 is controlled in response to the pressure of the suction chamber 25 introduced through the pressure-sensitive passage 38.

Therefore, the opening degree of the air supply passage 36 is adjusted by the capacity control valve 37, and the pressure in the crank chamber 15 is changed, so that the pressure in the crank chamber 15 acting before and after the piston 23 and the pressure in the cylinder bore 12a Is adjusted. As a result, the inclination angle of the cam plate 18 is changed, the stroke amount of the piston 23 is changed, and the discharge capacity is adjusted.

For example, when the cooling load is small, the suction pressure becomes lower than the set value, and the capacity control valve 37 is operated to increase the opening of the air supply passage 36. Therefore, the pressure of the crank chamber 15 is increased by the introduction of the refrigerant gas from the discharge chamber 26. Therefore, the hinge pin 21 of the hinge mechanism 20 is guided by the guide hole 33b while the axis L
, The cam plate 18 slides along the drive shaft 16, the inclination angle is changed to a minimum, and the stroke amount of the piston 23 is reduced. As a result, the discharge capacity is reduced, and the suction pressure is increased so as to approach the set value.

When the cooling load is large, the suction pressure becomes higher than the set value, and the capacity control valve 37 is operated so as to reduce the opening of the air supply passage 36. For this reason, the pressure in the crank chamber 15 is released to the suction chamber 25 via the bleed passage 35 and is reduced. Accordingly, the hinge pin 21 of the hinge mechanism 20 moves in the direction away from the axis L while being guided by the guide hole 33b, and the cam plate 18 slides along the drive shaft 16 so that the inclination angle becomes the maximum side. This is changed, and the stroke amount of the piston 23 increases. As a result, the discharge amount increases, and the suction pressure is reduced so as to approach the set value.

The effects that can be expected from the above embodiment will be described below. (1) The cam plate 18 is formed by joining and fixing a disk member 18a and a mooring member 18b formed by press molding. Therefore, the number of parts to be machined can be greatly reduced as compared with the conventional forming method in which a material formed by casting is cut. That is, the number of manufacturing steps can be reduced, and the time required for processing can be reduced. (2) Also, by using press molding, excess weight inevitable in integral molding by casting or the like can be eliminated, so that weight reduction can be achieved. (3) Since the disk member 18a and the mooring member 18b are formed by press molding, a high-strength material or a highly versatile material can be used as the material. Therefore, it is possible to make each part suitable material and proper production, and it is possible to enhance the reliability of quality.

The present invention is not limited to the above embodiment, but can be implemented as follows. 〇 For example, the mooring member 18b is shaped as shown in FIG. That is, the substantially U-shaped mooring member 1 is formed by press molding.
8b and the support arm 5 inclined with respect to the base 51
2, a pin hole 53 for inserting the hinge pin 21 is formed. A stop hole 54 is formed in the mooring member 18b, and by inserting a rivet through the stop hole 54, the disc member 1
8a. Even in such a configuration, substantially the same operation and effect as in the above embodiment can be exerted.

[0029]

According to the present invention having the above-mentioned structure, the cam plate can be formed more simply by using press molding for forming the constituent members of the cam plate.

[Brief description of the drawings]

FIG. 1 is a sectional view showing a variable displacement compressor according to the present invention.

FIG. 2 is a perspective view showing a main part.

FIG. 3 is a perspective view showing main components.

FIG. 4 is a perspective view showing main components.

FIG. 5 is a perspective view showing another embodiment.

FIG. 6 is a sectional view showing a conventional variable displacement compressor.

FIG. 7 is a perspective view showing a main part in a conventional example.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 11 Front housing which comprises a housing 12 Cylinder block which comprises a housing 13 Rear housing which comprises a housing 15 Crank chamber 16 Drive shaft 17 Rotation support 18 Cam plate 18a Disk member 18b Mooring member 20 Hinge mechanism 23 Piston

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Tomoji Tarutani 2-1-1 Toyota-cho, Kariya-shi, Aichi F-term in Toyota Industries Corporation (reference) 3H076 AA06 BB41 CC19

Claims (4)

[Claims] A cylinder bore and a crank chamber are formed in a housing and a drive shaft is supported, and a piston is housed in the cylinder bore. A rotary support is fixed to the drive shaft in the crank chamber. A cam plate is tiltably supported on the drive shaft, and a hinge mechanism is interposed between the rotating support and the cam plate. With the guidance of the hinge mechanism, the cam plate slides while tilting in the axial direction of the drive shaft. In the variable displacement compressor capable of changing a discharge capacity by being moved, the cam plate includes two or more members including an anchoring member forming a hinge mechanism and a disk member connected to the piston. A variable displacement compressor characterized in that at least one member is formed by press molding. 2. The variable displacement compressor according to claim 1, wherein the cam plate is formed by joining and fixing two members, a mooring member and a disk member. 3. The variable displacement compressor according to claim 1, wherein the disk member is formed by press forming. 4. The variable displacement compressor according to claim 1, wherein the mooring member is formed by press molding.