JP3399386B2 - Method of forming through hole of swash plate in variable capacity swash plate compressor - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a method of forming a through hole of a swash plate in a variable capacity swash plate compressor used in a vehicle air conditioner or the like.

[0002]

2. Description of the Related Art A conventional variable capacity swash plate compressor (hereinafter referred to as
Simply called a compressor. ), Japanese Patent Laid-Open No. 4-159464
The one described in Japanese Patent Publication is known. In this compressor, a cylinder bore is formed in a cylinder block, an intake chamber and a discharge chamber are formed in a housing, and a crank chamber is formed by joining them. In the crank chamber, the rotor is supported by the drive shaft so that the rotor can rotate synchronously, and the rotary drive body is pivotally supported by the hinge mechanism between the rotor and the drive shaft via the sleeve so that the rotary drive can rotate synchronously and can be tilted. Has been done. A rotary swash plate is fixed to the rotary drive,
A swash plate is formed by both. The hinge mechanism is equipped with a mounting hole provided in a support arm protruding from the rotor, a bearing having a guide hole penetrating through the mounting hole, and at least a tilting displacement in the front-rear direction, and a guide fixed to the rotary drive body. The guide pin is loosely fitted in the hole so as to reciprocate. Further, the sleeve is equipped so as to be slidable in the axial direction of the drive shaft, and the outer surface is provided with restriction surfaces extending in parallel to the axial direction, and the restriction surfaces are provided in a direction perpendicular to the axis. The pivot pin is projected. The rotary drive body is engaged with both pivot pins while abutting both restricting surfaces of the sleeve. Pistons are engaged with the rotary swash plate via a pair of shoes that convert swinging motion based on the tilt angle of the rotary swash plate into reciprocating motion, and each piston is housed in each cylinder bore. The cylinder block is provided with a bleed passage which connects the crank chamber and the suction chamber, and the bleed passage is opened and closed by a control valve.

In this compressor, when the rotary drive body and the rotary swash plate rotate at a predetermined tilt angle as the drive shaft is driven, the piston reciprocates in the cylinder bore. As a result, the refrigerant gas is sucked into the cylinder bore from the suction chamber, and the refrigerant gas is compressed and then discharged to the discharge chamber. Then, the tilt angle of the rotary swash plate and the rotary drive body is displaced by adjusting the pressure in the crank chamber by the control valve, and thereby the discharge capacity of the refrigerant gas discharged to the discharge chamber is controlled.

At this time, in cooperation with the hinge mechanism, the sleeve slides axially with respect to the drive shaft, so that the rotary drive body slides axially with respect to the drive shaft and, at the same time, is provided on the sleeve. The rotary drive is tilted about the center of the pivot pin. In addition, the rotary drive body and the rotary swash plate receive a moment to incline the center of the axis from the direction perpendicular to the axis due to the compression reaction force and the suction force of the refrigerant gas through the piston and the shoe. It is received by the mechanism or by abutment of the rotary drive with the restricting surface of the sleeve, which prevents tilting of the swash plate with respect to the pivot center.

[0005]

However, in the above-mentioned conventional compressor, the swash plate is rotationally driven because the rotary swash plate is fixed to the rotary drive body that engages with the pivot pin in order to tiltally displace the swash plate. It is composed of a body and a rotary swash plate, and has a large number of parts, and also has a large axial length due to the required axial length of the rotary drive body and the like.

Further, in this compressor, a sleeve is provided between the swash plate and the drive shaft, and a pivot pin is provided on the sleeve in order to receive the moment due to the inclination displacement of the swash plate and the compression reaction force. Therefore, the number of parts is increased by the amount corresponding to the sleeve and the pivot pin. For this reason, this compressor has the drawbacks of high manufacturing cost due to the large number of parts, and troublesome parts management, etc., and lack of mountability on a vehicle or the like due to the large axial length. It also has the drawback.

An object of the present invention is to easily form a through hole in order to manufacture a variable capacity type swash plate compressor capable of reducing the number of parts and shortening the shaft.

[0008]

In the method of forming a through hole of a compressor according to the present invention, in order to solve the above-mentioned problems, a crank chamber, a suction chamber, a discharge chamber and a cylinder bore connected to these are defined in a housing. In addition, a piston is housed in each of the cylinder bores so as to be able to reciprocate, and a rotor positioned in the crank chamber is supported for synchronous rotation on a drive shaft supported by the housing, and the rotor and hinge mechanism are also supported. A swash plate connected via a through hole is fitted to the swash plate such that the tilt angle can be changed, and a connection is provided between the swash plate and the piston for converting the back-and-forth swinging motion of the swash plate into reciprocating motion of each piston. How to form the through hole of the swash plate in a variable displacement type swash plate compressor in which a mechanism is interposed and the inclination of the swash plate is controlled by the pressure in the crank chamber to change the discharge capacity In the through hole of the swash plate, a drill is performed along the first center line to form a circular hole, an end mill having the same diameter is inserted into the circular hole, and the end mill is rotated. , The swash plate up to a second center line centered on a pivot center extending beyond the drive shaft on the side facing the hinge mechanism with the shaft center interposed therebetween. By rotating , the pivot is placed in the through hole.
A new configuration is adopted in which a circular arc-shaped support portion is formed as the center.

The swing angle between the first center line and the second center line is preferably larger than the displaceable angle which is the difference between the maximum tilt angle and the minimum tilt angle of the swash plate. In the compressor according to the present invention, the swash plate connected to the rotor via the hinge mechanism is fitted to the through hole so that the drive shaft can be tilted and displaced. The through hole is formed so as to allow the tilt displacement of the swash plate over the entire control range, centering on the center of the pivot set over the drive shaft on the side facing the hinge mechanism with the shaft center in between. In the through hole thus formed, a supporting portion is formed in an arc shape centered on the center of the pivot, and a restriction surface extending parallel to the axis is formed flat on the side surface.

Therefore, when the drive shaft is fitted into the through hole, the swash plate itself slides in the axial direction with respect to the drive shaft in cooperation with the hinge mechanism, and at the same time, the support in the through hole is performed. The swash plate is tilted by the part. Therefore, in this compressor,
Since the swash plate itself is tilt-displaced, it is not necessary to configure the swash plate with a large rotary drive and a rotary swash plate as in the conventional case.

Also in this compressor, the swash plate receives a moment to rotate the center of the pivot from the direction perpendicular to the axis due to the compression reaction force and the suction force of the refrigerant gas through the piston and the connecting mechanism. Such a moment is received by the hinge mechanism or by the contact between the restricting surface in the through hole and the peripheral surface of the drive shaft, whereby the inclination of the swash plate with respect to the center of the pivot is prevented. For this reason, it is not necessary to provide a sleeve and a pivot pin between the swash plate and the drive shaft, unlike the conventional case, in order to receive a moment due to an inclination displacement of the swash plate and a compression reaction force.

Since the through hole can be formed by gently bending the circular hole with a drill, an end mill or the like, it is easy to form. Further, since the support portion in the through hole is formed in an arc shape, the peripheral surface of the drive shaft always keeps line contact with the support portion, and the support portion is less likely to be worn. In this respect,
Japanese Patent Publication No. 31234/1993 also discloses a compressor in which a swash plate is provided with a through hole and a drive shaft is inserted into the through hole. The through hole of the compressor is a circular hole. Is bent with a narrow angle, and since the peripheral surface of the drive shaft comes into contact with the support portion at a narrow angle, the support portion is easily worn.

Therefore, in the compressor according to the present invention, it is not necessary to form the swash plate with the rotary driving body and the rotary swash plate as in the conventional case, and the sleeve and the drive shaft are provided between the swash plate and the drive shaft as in the conventional case. Since it is not necessary to provide a pivot pin, the number of parts can be reduced. Therefore, the manufacturing cost can be reduced and the parts management can be facilitated.

Further, in this compressor, the shaft can be shortened by the amount of the conventional rotary drive member, so that the compressor can be excellently mounted on a vehicle or the like. Furthermore, in this compressor, since the support portion of the swash plate that contacts the drive shaft is less likely to be worn, the inclination angle of the swash plate is reliably ensured,
And it can exhibit excellent durability.

Further, in this compressor, since the through hole can be easily formed by a drill or the like, the manufacturing cost can be further reduced.

[0016]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. In this compressor,
As shown in, the front housing 2 is joined to the front end side of the cylinder block 1, and the rear housing 3 is joined to the rear end side via the valve plate 4. A drive shaft 6 extending in the X-axis direction is housed in a crank chamber 5 formed by the cylinder block 1 and the front housing 2, and the drive shaft 6 is rotatably supported by bearings 7a and 7b. A plurality of cylinder bores 8 are formed in the cylinder block 1 at positions surrounding the drive shaft 6,
A piston 9 is fitted in each cylinder bore 8.

In the crank chamber 5, a rotor 10 is supported on the drive shaft 6 by a bearing 8 between the drive shaft 6 and the front housing 2 so as to be rotatable in synchronism with the drive shaft 6, and behind the rotor 10 is a through hole 20. A swash plate 11 having the drive shaft 6 inserted therein is provided. As shown in FIG. 2, the through hole 20 of the swash plate 11 is first drilled along the center line l ₁ to form a circular hole. Then, an end mill having the same diameter is inserted into the circular hole, and while rotating the end mill, it extends in a direction perpendicular to the axis X and the drive shaft 6 on the side facing the hinge mechanisms K, K with the axis X interposed therebetween. The swash plate 11 is rotated up to the center line l ₂ around the axis center Y set to exceed. In this way, the circular hole formed by the end mill is gently bent around the center Y of the axis, whereby the through hole 20 is easily formed. The through hole 20 can be formed by the reverse operation.

The swing angle Θ between the center line l ₁ and the center line l ₂ is the parallel plane L of the swash plate 11 at the maximum tilt angle shown in FIG.
_{As shown by 1} and the parallel surface L ₂ of the swash plate 11 at the minimum tilt angle shown in FIG. 3, it is slightly larger than the displaceable angle θ which is the difference between the maximum tilt angle and the minimum tilt angle. Specifically, the swing angle Θ is ₁ to 2 closer to the center line l ₁ than the displaceable angle θ.
Is increased by 10 ° to 15 ° on the side of the center line l ₂ .

As shown in FIGS. 4 and 5, a support portion 20b is formed in an arc shape around the center Y of the axis and extends in parallel with the axis X in the through hole 20 thus formed. The regulation surfaces 20a, 20a are formed flat on the side surfaces. If the axis center Y is set far beyond the drive axis 6,
Be careful because it affects the variable characteristics and top clearance fluctuations.

As shown in FIG. 1, a pressing spring 12 is interposed between the rotor 10 and the swash plate 11, and the pressing spring 12 urges the swash plate 11 toward the rear housing 3. . Also, hemispherical shoes 14, 14 as a connecting mechanism are in contact with the outer peripheral portion of the swash plate 11, and the outer peripheral surfaces of these shoes 14, 14 are engaged with the ball bearing surface of the piston 9. . Thus, the shoes 14, 14 are attached to the swash plate 11.
A plurality of pistons 9, which are moored via, are housed in each cylinder bore 8 so as to be able to reciprocate.

On the front surface of the swash plate 11, as shown in FIG.
Hinge mechanism K, a pair of brackets 15 and 1 constituting the K
5 is projectingly provided so as to straddle the top dead center position T of the swash plate 11 with the drive shaft 6 interposed therebetween, and one end of the guide pin 16, 16 is fixed to each bracket 15, 15. Ball portions 16a, 16a are fixed to the other ends of 16, 16. In addition, the hinge mechanism K,
A pair of support arms 17, 17 forming the remaining part of K are projected rearward in the axial X direction so as to face the guide pins 16, 16. The tip ends of the support arms 17, 17 are parallel to the plane determined by the axis X of the drive shaft 6 and the top dead center position T of the swash plate 11, and with respect to the axis X of the drive shaft 6. The guide holes 17a, 17a are linearly provided so as to approach from the outside. The directions of the center lines of these guide holes 17a, 17a are set so that the top dead center position of the piston 9 is hardly displaced forward and backward regardless of the inclination displacement of the swash plate 11. As shown in FIG. 1, spherical portions 16a, 16a of the guide pins 16, 16 are rotatably and slidably inserted in the guide holes 17a, 17a, respectively.

The inside of the rear housing 3 is divided into a suction chamber 30 and a discharge chamber 31. A suction port 32 and a discharge port 33 are formed in the valve plate 4 so as to correspond to each cylinder bore 8, and a compression chamber formed between the valve plate 4 and the piston 9 connects the suction port 32 and the discharge port 33. It communicates with the suction chamber 30 and the discharge chamber 31 via the. Each suction port 32 is provided with a suction valve (not shown) that opens and closes the suction port 32 in response to the reciprocating movement of the piston 9.
3 is provided with a discharge valve (not shown) that opens and closes while restricting the discharge port 33 by the retainer 34 according to the reciprocating movement of the piston 9. Further, the rear housing 3 is equipped with a control valve (not shown) for adjusting the pressure of the crank chamber 5.

In the compressor configured as described above,
When the swash plate 11 rotates in accordance with the drive of the drive shaft 6 shown in FIG. 1, each piston 9 reciprocates in the cylinder bore 8 via the shoes 14, 14, whereby refrigerant gas is sucked from the suction chamber 30 into the compression chamber. The refrigerant gas is sucked, compressed, and then discharged into the discharge chamber 31. At this time, the discharge capacity of the refrigerant gas discharged into the discharge chamber 31 is determined by the control valve in the crank chamber 5
It is controlled by adjusting the internal pressure.

That is, in the state of FIG. 2, if the pressure in the crank chamber 5 rises due to the pressure adjustment of the control valve, the back pressure acting on the piston 9 rises, and the tilt angle of the swash plate 11 decreases. That is, the spherical portions 16a, 16a of the guide pins 16, 16 in the hinge mechanisms K, K are not connected to the guide holes 1
7a, 17a is rotated counterclockwise, and the center of the guide hole 17a, 17a is X from the outside along the center line.
Slide toward the side. Further, the swash plate 11 rotates counterclockwise while bringing the peripheral surface of the drive shaft 6 into contact with the support portion 20b having the pivot center Y as the center, and bends to the pressing spring 12 and retreats. As a result, the inclination angle of the swash plate 11 becomes smaller, and the state changes to the state shown in FIG. 3, the stroke of the piston 9 is reduced, and the discharge capacity is reduced.

On the contrary, in the state of FIG. 3, if the pressure in the crank chamber 5 is lowered by adjusting the pressure of the control valve, the back pressure acting on the piston 9 is lowered, and the inclination angle of the swash plate 11 is increased. That is, the ball portions 16a and 16a of the guide pins 16 and 16 in the hinge mechanisms K and K have the guide holes 17
While rotating in the a and 17a in the clockwise direction, the guide holes 17a and 17a slide in the guide holes 17a and 17a in the direction away from the center X along the center line. In addition, the swash plate 11 is attached to the support portion 20.
While the peripheral surface of the drive shaft 6 is brought into contact with b, the drive shaft 6 rotates clockwise and moves forward against the pressing spring 12. This allows
Since the inclination angle of the swash plate 11 becomes large, the state changes to the state shown in FIG. 2, the stroke of the piston 9 is extended, and the discharge capacity becomes large.

Therefore, in this compressor, since the swash plate 11 itself is tilt-displaced at the displaceable angle θ, it is not necessary to configure the swash plate with a large rotary drive and a rotary swash plate as in the conventional case. . Also in this compressor, a moment acts on the swash plate 11, but the moment is mostly received by the pair of hinge mechanisms K, K, and the restricting surfaces 20a, 20a in the through hole 20 and the drive shaft 6 are prevented. The inclination of the swash plate 11 with respect to the center Y of the axis is prevented without imposing a heavy load on the peripheral surface. Therefore, in order to receive the moment due to the inclination displacement of the swash plate 11 and the compression reaction force, it is not necessary to provide the sleeve and the pivot pin between the swash plate and the drive shaft as in the conventional case.

Therefore, in this compressor, since the conventional rotary driver, rotary swash plate, sleeve, and two pivot pins can be covered by one swash plate 11, the manufacturing cost can be reduced by the reduced number of parts. It is possible to realize simplification of parts management and the like. Further, in this compressor, the shaft can be shortened by the amount of the conventional rotary drive body, and the moment due to the compression reaction force or the like is mostly received by the pair of hinge mechanisms K, K, and the moment is generated in the through hole 20. The shaft is shortened by adopting a thin swash plate 11 by not accepting the swash plate, and the swash plate 11 and the piston 9 are paired by the pair of shoes 14, 14.
Since the shaft is shortened by connecting a general swing plate by connecting and, it is possible to exhibit excellent mountability on a vehicle or the like.

The swash plate 11 has a circlip 13 in which a rear end surface 11b formed in a concave shape at the rear portion of the through hole 20 is locked to the drive shaft 6 in the extended state of the pressing spring 12 shown in FIG. By contacting with, the further tilting in the tilt angle reducing direction is restricted. On the other hand, in the swash plate 11 in the most contracted state of the pressing spring 12 shown in FIG. 2, the front end surface 11a formed in a slanting shape in the lower portion abuts the rear end surface 10a of the rotor 10 to increase the inclination angle. Further tilting is regulated.

During this time, since the swing angle Θ is set to be slightly larger than the displaceable angle θ, as shown in FIG. 2, the front lower surface 20c and the rear upper surface 2 of the through hole 20 at the maximum inclination angle.
0d does not contact the peripheral surface of the drive shaft 6. Further, as shown in FIG. 3, the rear lower surface 20e and the front upper surface 20f of the through hole 20 do not come into contact with the peripheral surface of the drive shaft 6 at the minimum inclination angle. That is, the through hole 20 does not maintain the maximum tilt angle and the minimum tilt angle, and the gap between the through hole 20 and the drive shaft 6 is large.

Therefore, in this compressor, as shown in FIG. 5, the guide shafts 17a, 1a are provided while the drive shaft 6 is brought into contact with the rear lower surface 20e and the front upper surface 20f, for example.
Since the spheres 16a, 16a can be easily inserted into the 7a, the swash plate 1 can be inserted after the rotor 10 is press-fitted into the drive shaft 6.
1 can be assembled. Therefore, in this compressor, excellent assembling property is ensured, and the manufacturing cost can be reduced.

In this compressor, since the support portion 20b in the through hole 20 is formed in an arc shape, the drive shaft 6
The peripheral surface of is always in line contact with the supporting portion 20b,
b is not easily worn. Further, since the moment due to the compression reaction force or the like can be almost received by the pair of hinge mechanisms K, K, the regulating surfaces 20a, 20a of the swash plate 11 are also less likely to be worn. Further, since the gap between the through hole 20 and the drive shaft 6 is large, the force for maintaining the inclination angle of the swash plate 11 is not received by the through hole 20 of the swash plate 11. The entire through hole 20 is hard to be worn. Therefore, in this compressor, the tilt angle of the swash plate 11 can be reliably ensured, and excellent durability can be exhibited.

Further, in this compressor, since the through hole 20 can be provided by gently bending the circular hole by a drill, an end mill, etc., the through hole 20 can be easily formed. Therefore, in this compressor, the manufacturing cost can be further reduced. During the operation of the compressor, a compression reaction force or the like acts on the swash plate 11, and the support portion 20b is constantly pressed against the peripheral surface of the drive shaft 6, so that the through hole 20 and the drive shaft 6 are There is no rattling due to such a gap.

[Brief description of drawings]

FIG. 1 is a vertical sectional view of a compressor according to an embodiment.

FIG. 2 is a cross-sectional view of relevant parts of the compressor according to the embodiment at the maximum tilt angle.

FIG. 3 is a cross-sectional view of relevant parts of the compressor according to the embodiment at a minimum tilt angle.

FIG. 4 is an exploded plan view showing a hinge mechanism according to the compressor of the embodiment.

FIG. 5 is an enlarged cross-sectional view of a main part of the swash plate according to the compressor of the embodiment.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Cylinder block 2 ... Front housing 3 ... Rear housing 5 ... Crank chamber 30 ... Suction chamber 31 ... Discharge chamber 8 ... Cylinder bore 9 ... Piston 6 ... Drive shaft 10 ... Rotor K ... Hinge mechanism 11 ... Swash plate 14 ... Shoe (connection) Mechanism) 20 ... Through hole 20b ... Support portion 20a ... Restricting surface T ... Top dead center position X ... Axis center Y ... Axis center l ₁ ... First center line l ₂ ... Second center line

─────────────────────────────────────────────────── ─── Continuation of the front page (56) Reference JP-A 63-205470 (JP, A) JP-A 5-106552 (JP, A) JP-A 4-22772 (JP, A) JP-A 4- 159464 (JP, A) JP 63-186973 (JP, A) JP 61-255285 (JP, A) JP 61-171886 (JP, A) Actual Kaihei 6-67869 (JP, U) Japanese Patent Publication 1-25900 (JP, B2) (58) Fields investigated (Int.Cl. ⁷ , DB name) F04B 27/08

Claims (2)

(57) [Claims] 1. A crank chamber, a suction chamber, a discharge chamber, and a cylinder bore connected to these are defined and formed in a housing, and a piston is reciprocally housed in each cylinder bore and supported by the housing. A rotor positioned in the crank chamber is rotatably supported on the drive shaft in a synchronous manner, and a swash plate connected to the rotor via a hinge mechanism is fitted through a through hole so that the tilt angle of the swash plate is variable. A coupling mechanism for converting the back-and-forth swinging motion of the swash plate into a reciprocating motion of each piston is interposed between the piston and the piston, and the inclination angle of the swash plate is controlled by the pressure in the crank chamber to control the discharge capacity. A method of forming the through hole of the swash plate in a variable capacity swash plate compressor configured to change, wherein the through hole of the swash plate is drilled along a first center line. Circle A hole is formed, an end mill having the same diameter is inserted into the circular hole, the end mill is rotated, the end mill extends in a direction perpendicular to the axis, and the drive on the side facing the hinge mechanism with the axis interposed therebetween. around a set pivot center than the shaft, before by rotating the swash plate to the second center line
A method of forming a through hole in a variable capacity type swash plate compressor characterized by forming an arcuate support part centering on a pivot in the through hole " 2. The swing angle between the first center line and the second center line is larger than the displaceable angle which is the difference between the maximum tilt angle and the minimum tilt angle of the swash plate. Item 3. A method of forming a through hole in a variable capacity swash plate compressor according to Item 1 or 2.