JPH10227281A - Smash plate compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a swash plate compressor having a simple and inexpensive lubrication structure which can supply a librication oil stably and surely and improve the reliability of a seal part. SOLUTION: A front housing 20 has an oil passage 20a penetrated to a crank room 15 and around a drive shaft 3 and an oil sump means 19 for receiving the lubrication oil is provided in the entrance part of the oil passage 20a so as to scratch up the lubrication oil of the crank room 15 by the rotation of the drive shaft 3 and supply the lubrication oil to the drive shaft 3 through the oil passage 20a. The oil sump means 19 is composed of one part of a first thrust race 201b' and an oil receive groove 20g.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a swash plate type compressor used for, for example, an air conditioner of an automobile, and more particularly to a swash plate type compressor having a structure for supplying lubricating oil to a bearing portion supporting a drive shaft. It belongs to the plate type compressor.

[0002]

2. Description of the Prior Art FIG. 6 shows a conventional swash plate type compressor. The swash plate compressor 1 includes a housing 2 and a drive shaft 3.
, A swash plate 4, a piston 5, a pair of substantially hemispherical shoe members 6, and the like.

The housing 2 includes a front housing 20 having a substantially funnel shape, a housing body 21 having a substantially cylindrical shape, and a cylinder head 22 having a substantially cup shape. .

[0004] The front housing 20 has a cylindrical shaft through hole 210 through which the drive shaft 3 passes. The front housing 20 is provided with a first radial needle bearing 200, a thrust needle bearing member 201, and a shaft seal member 202. The shaft seal member 202 and the first radial needle bearing 200 are provided between the inner wall of the shaft through hole 210 and the drive shaft 3.

[0005] On one opening side of the housing body 21,
A crank chamber 15 is formed, one open end of which is closed by a front housing 20. The other open end of the housing body 21 opposite to the one open end is closed by the cylinder head 22 with the valve plate device 24 interposed therebetween. The cylinder block 23 has a center hole 230 and a plurality of cylinder bores 231 formed around the center hole 230. Multiple cylinder bores 2
Reference numerals 31 are formed in the cylinder block 23 at an angular interval from each other around the axis.

[0006] The drive shaft 3 is inserted into the center hole 230. The drive shaft 3 is arranged via a second radial needle bearing 232. Cylinder bore 23
Reference numeral 1 denotes an outer peripheral portion of the cylinder block 23 and a central hole 2
A plurality are formed at equal intervals so as to surround 30. Further, the cylinder head 22 includes a suction chamber 22.
0 and a discharge chamber 221 are formed.

The above-described front housing 20 is fixed to the housing main body 21 by a plurality of first bolts 25. The cylinder head 22 is fixed to the housing main body 21 by a plurality of second bolts 26 with the valve plate device 24 interposed therebetween.

That is, the front housing 20, the housing body 21, and the cylinder head 22 are integrally fixed to each other by the first and second bolts 25 and 26 to form the housing 2.

The first bolt 25 is connected to the housing body 21.
In the vicinity of the inner peripheral wall of the cylinder bore 231, it extends in parallel with the center line of the cylinder bore 231 and is inserted so as to pass between adjacent cylinder bores 231.

The drive shaft 3 is rotatably supported by the front housing 20 and the cylinder block 23 via first and second radial needle bearings 200,232. This drive shaft 3 is located at the center of the housing 2. One end of the drive shaft 3 protrudes from a shaft through hole 210 of the front housing 20 to the outside. The distal end portion of the drive shaft 3 projecting to the outside is configured to transmit, for example, a force from an engine (not shown) via an electromagnetic clutch (not shown).

The swash plate 4 is hinged to a rotor 9 fixed to the drive shaft 3 via an arm member 13.
That is, the swash plate 4 rotates together with the drive shaft 3. The swash plate 4 has a spherical bush 8 mounted on the drive shaft 3 interposed therebetween. The spherical bush 8 is mounted on the drive shaft 3 so as to make the inclination angle with respect to the drive shaft 3 variable.
Further, the swash plate 4 is connected to a rotor 9 fixed to the drive shaft 3. As a result, the swash plate 4 rotates with the drive shaft 3.

A coil spring 10 mounted on the drive shaft 3 is interposed between the swash plate 4 and the rotor 9. The swash plate 4 is urged by the coil spring-in 10 so that the inclination angle of the swash plate 4 becomes smaller. The rotor 9 is connected to the swash plate 4 by an arm member 13.
Of the arm member 13 is hingedly connected to the rotor 9. Further, the rotor 9 has a balance member 9 a on the side opposite to the arm member 13. This rotor 9
It is held on the inner wall surface of the front housing 20 via a thrust needle bearing member 201.

Thrust needle bearing member 201
Is composed of a bearing 201a, a substantially disk-shaped first thrust trace 201b, and a substantially disk-shaped second thrust trace 201c.

The first and second thrust traces 201b, 201b,
201c sandwiches the bearing 201a. The drive shaft 3 penetrates through the first thrust trace 201 b and is located on the inner wall surface of the front housing 20. The second thrust trace 201c is assembled on the front surface of the rotor 9.

Each of the plurality of pistons 5 incorporated into the plurality of cylinder bores 231 in one-to-one correspondence has a piston portion 50, a rod portion 51, and a shoe receiving portion 52.

The piston portion 50 is slidably inserted into the cylinder bore 231. The rod part 51 connects the piston part 50 and the shoe receiving part 52. The shoe receiving portion 52 has a shoe receiving surface 52a that is concave in a spherical shape.

Here, the pair of shoe members 6 slidably hold the outer peripheral end of the swash plate 4 so as to sandwich it in the thickness direction. Each of the shoe members 6 is slidably disposed on a shoe receiving portion 52 of the piston 5 and slidably sandwiches the swash plate 4. With this configuration, the shoe member 6 transmits only the reciprocating linear motion to the shoe receiving portion 52 from the swinging motion performed by the rotation of the swash plate 4 together with the drive shaft 3, and causes the piston portion 50 to move within the cylinder bore 231. It is designed to reciprocate linearly.

The reciprocating linear motion of the piston portion 50 in the cylinder bore 231 causes the refrigerant gas to flow into the suction chamber 220.
Through the valve plate device 24 and the piston portion 50
The compressed gas is discharged to the discharge chamber 221 through the valve plate device 24.

Lubricating oil is stored in the crank chamber 15 in order to smooth the movement of various parts of the compressor.
The lubricating oil is scooped up by the rotor 9 and the swash plate 4 that rotate together with the drive shaft 3 to the inner wall surface of the crank chamber 15 and blown off. The lubricating oil flows to various parts and the inner wall surface to smooth the movement.

Incidentally, the radial needle bearing 2
00 and the shaft seal member 202 are not provided in the crankcase 15. Therefore, in the front housing 2, an oil passage 20a is provided between the crank chamber 15 and the shaft through-hole 210 in order to keep the smooth movement of the radial needle bearing 200 and the shaft seal member 202 and to effectively maintain the sealing performance. Is formed.

The lubricating oil stored in the crank chamber 15 is swept up by the rotation of the drive shaft 3 in the oil passage 20a, and the lubricating oil is supplied to the shaft through hole 210 through the oil passage 20a.

That is, the lubricating oil on the inner wall surface of the crank chamber 15 is supplied to the shaft through hole 210 through the oil passage 20a to the radial needle bearing 200 and the shaft seal member 202.

The front housing 2 on the crank chamber 15 side
A large large-diameter groove 204 extending radially around the shaft through hole 210 is formed on the inner wall surface of the zero. Large diameter groove 20
4 is an inner wall surface of the front housing 20 and a balance member 9
a so as to rotate the rotor 9 without interfering with the shaft through hole 210. The rotor 9 is provided with a balance member 9a projecting from the thrust needle bearing member 201 toward the large-diameter groove 204. The balance member 9a and the inner wall surface of the front housing 20 are configured to be close to each other. The balance member 9
“a” has its tip extending to the vicinity of the bottom surface of the large-diameter groove 204.

Further, on the inner wall surface of the front housing 20, an oil receiving groove 20 g long in the radial direction is formed on a part of the circumference of the first thrust trace 201 b in the radial direction and on a part of the bottom of the large diameter groove 204. Are formed. One inlet of the oil passage 20a is located in the oil receiving groove 20g. Oil receiving groove 2
One inlet of 0 g is located in the oil receiving groove 20 g and is located radially outside of the first thrust trace 201 b.

The lubricating oil flows on the inner wall surface of the front housing 20, and flows from the oil receiving groove 20g to the oil passage 20a.

[0026]

As described above, the rotor 9 is provided with the bounce member 9 protruding into the large-diameter groove 204.
a, and the inner surface of the front lance 20 and the inner wall surface of the front housing 20 are close to each other.

Therefore, the lubricating oil on the inner wall surface side of the front housing 20 is blown out in the outer diameter direction by the centrifugal force generated by the rotation of the rotor 9, and lubricating the bearing portion that is the radial needle bearing 200 and the shaft seal member 202. Insufficient oil supply.

Therefore, in the shaft seal member 202, the lubrication is insufficient and a stable sealing property cannot be obtained. Therefore, the gas in the crank chamber 15 flows out of the front housing 20 from the shaft seal member 202 through the shaft through hole 210. It is a cause of leakage.

Therefore, an object of the present invention is to form a simple and inexpensive lubricating structure, to supply a stable and reliable lubricating oil,
An object of the present invention is to provide a swash plate compressor capable of improving the reliability of a seal portion.

[0030]

According to the present invention, there is provided a housing having a plurality of cylinder bores formed at an angular interval from each other around an axis, a housing having a crank chamber adjacent to the cylinder bore, A drive shaft rotatably supported by the housing and extending to the housing; a swash plate mounted on the crank chamber so as to be inclined with respect to the drive shaft and rotated with the drive shaft; A plurality of pistons each slidably inserted into the cylinder bore, and a member that converts the swinging motion of the swash plate into a linear reciprocating motion of the piston and transmits the same, and the housing includes the drive shaft. A shaft through-hole having a radial bearing rotatably supported, and an oil passage penetrating the crank chamber and the shaft through-hole. In a swash plate type compressor for scooping up the lubricating oil in the rank chamber and supplying the lubricating oil through the oil passage to the bearing portion of the drive shaft, oil retaining means for receiving the lubricating oil is provided at an inlet of the oil passage. A swash plate compressor characterized by the following is obtained.

[0031]

According to the swash plate type compressor of the present invention, an oil retaining portion for receiving lubricating oil is provided at an inlet portion of an oil passage, or a thrust trace having a diameter equal to or larger than that of the rotor is arranged, thereby causing rotation of the rotor. By centrifugal force,
The shortage of lubricating oil for the bearing portion can be compensated.

[0032]

FIG. 1 is a longitudinal sectional view of a swash plate type compressor according to a first embodiment of the present invention. FIG. 2 is a sectional view of the swash plate type compressor shown in FIG. 3 taken along line III-III. FIG. 4 is a sectional view taken along line IV-IV in FIG.

FIG. 1 shows a cross section taken along the line II-II of FIG. Hereinafter, in describing the embodiment of the present invention, the same configuration and the same parts as those of the conventional swash plate type compressor shown in FIG. Descriptions of parts other than are omitted.

First, referring to FIGS. 1 and 2, the swash plate type compressor has an oil retaining portion formed at an inlet portion of an oil receiving groove 20g for securing lubricating oil flowing into oil passage 20a. 19. The oil retaining portion 19 is provided with the oil receiving groove 2.
0 g and a portion extending in the radial direction of the first thrust trace 201 b ′, which is a component of the thrust needle bearing member 201. That is,
The oil retaining portion 19 is formed by a part of the first thrust trace 201b 'and the oil receiving groove 20g.

One inlet of the oil passage 20a is located in the oil receiving groove 20g.
Is formed between the first thrust trace 201b ′ extending in the radial direction along the bottom surface of the oil receiving groove 20g and the lower portion of the oil receiving groove 20g.

Incidentally, the oil retaining portion 19 is provided with the balance member 9.
The diameter is equal to or larger than the outer diameter of the balance member 9a.

The lubricating oil is blown off by the centrifugal force of the rotor 9 and is reliably secured in the oil reservoir 19. Lubricating oil is
The shaft seal member 202 and the radial needle bearing 20 pass through the shaft through hole 210 from the oil passage 20a having the inlet portion.
0.

Further, as shown in FIGS. 2 and 3, two lace bent portions 201d which are bent toward the bottom surface of the large-diameter groove 204 are formed on the periphery of the first thrust trace 201b '. .

The two race bent portions 201d in this embodiment are located at two peripheral portions on the diametrical line of the first thrust trace 201b ', and the plate surface of the first thrust trace 201b' is formed. It is bent almost at right angles.

On the bottom surface of the large-diameter groove 204 of the front housing 20, there are formed two fitting holes 20h for allowing the two race bent portions 201d to enter one-to-one. Each of the fitting holes 20h has a lace bending portion 201.
By fitting d with some degree of freedom, rotation of the first thrust trace 201b is prevented.

Therefore, the width of the race bending portion 201d is smaller than the diameter of the fitting hole 20h.
The dimension of the race bent portion 201d from the plate surface to the tip of the first thrust trace 201b '
h is smaller than the depth dimension.

In this embodiment, the first
Of the thrust trace 201b 'extends radially over the entire circumference.

However, the oil receiving groove 20g may be configured so as to be partially protruded in the radial direction so as to be covered by a part of the first thrust trace 201b. Hereinafter, this embodiment will be described as a second embodiment.

FIG. 4 is a sectional view of a swash plate type compressor according to a second embodiment of the present invention. FIG. 5 is a sectional view of the swash plate type compressor shown in FIG. 4 taken along line VI-VI.

Hereinafter, in describing a second embodiment of the present invention, the same parts as those of the swash plate type compressor shown in FIGS. 1, 2 and 3 are denoted by the same reference numerals. A description of parts other than the constituent parts that are the main parts of the second embodiment is omitted. Hereinafter, a configuration that is a main part of the present invention will be described.

Referring to FIGS. 4 and 5, an oil reservoir 19 for receiving lubricating oil is provided at the inlet of oil passage 20a. The oil retaining portion 19 is formed by an oil receiving groove 20 g and a portion extending in a radial direction from a part of a first thrust trace 201 b ″ which is one component of the thrust needle bearing member 201. The oil retaining portion 19 includes a part of the first thrust trace 201b ″ and an oil receiving groove 20g.
And is constituted by.

One opening of the oil passage 20a is located in the oil receiving groove 20g. The oil retaining portion 19 is formed between the first thrust trace 201b ″ and the lower portion of the oil receiving groove 20g. The oil receiving groove 20g is covered by an additional portion 201f that partially extends radially from a part of the outer peripheral end of the first thrust trace 201b ''.

Further, as shown in FIG. 5, one race bent portion 201d bent toward the bottom surface of the large-diameter groove 204 is formed on the periphery of the first thrust trace 201b ''.

The lace bending portion 2 in this embodiment is
01d is located at a peripheral portion on a diametrical line of the first thrust trace 201b '', and is bent at a substantially right angle from the plate surface of the first thrust trace 201b ''.

The large-diameter groove 2 of the front housing 20
One fitting hole 20h is formed on the bottom surface of the hole 04 so that each of the lace bent portions 201d can be inserted one-to-one. Each of the fitting holes 20h has a lace bending portion 201.
By fitting d with some degree of freedom, the rotation of the first thrust trace 201b '' is prevented.

The width of the race bent portion 201d is smaller than the diameter of the fitting hole 20h, and the dimension of the race bent portion 201d from the plate surface to the end of the first thrust trace 201b is smaller than the fitting hole. The dimension is smaller than the depth dimension of 20h.

As described in the first and second embodiments, the oil receiving groove 20g is provided in the front housing 20.
In order to receive the oil flow efficiently on the inner wall of the compressor, it is necessary to consider that the compressor is arranged so as to be located above the compressor when disposing the compressor.

Further, the swash plate type compressor according to the first and second embodiments has been described with reference to the configuration of the variable capacity type swash plate type compressor. Can also be applied.

The plurality of pistons 5 in this embodiment are single-headed pistons 5 each having a piston portion 50 slidably inserted into a plurality of cylinder bores 231. The shoe member 6 is a member that converts and transmits the linear reciprocating motion of the single-headed piston 5, and is held by the single-headed piston 5 so as to sandwich the swash plate 4.

The present invention is also applicable to a compressor having two cylinder blocks 23 on both sides of the swash plate 4. In this compressor, a double-headed piston is arranged in each of two cylinder blocks 23. Double-ended piston
It has two piston parts, and the double-headed piston is
2, two piston portions are respectively incorporated in the cylinder bores of the cylinder blocks on both sides. Two cylinder heads are provided in the cylinder blocks on both sides.

[0056]

According to the swash plate type compressor of the present invention, the oil retaining portion for receiving the lubricating oil is provided at the inlet portion of the oil passage so that the lubricating oil can be stably and surely passed through the shaft through-hole and the shaft seal member and the radial needle bearing. Can be supplied efficiently.

Further, since the oil retaining portion is constituted by one part of the thrust needle bearing and the oil receiving groove, it is possible to obtain excellent economy and sufficient reliability.

Therefore, it is possible to provide a compressor that is free from gas leakage, has excellent sealing properties, and is more effective at high speeds in response to market trends requiring high speeds.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a swash plate type compressor according to a first embodiment of the present invention.

FIG. 2 is a sectional view of the swash plate type compressor shown in FIG. 1, taken along the line III-III.

FIG. 3 is a sectional view of the swash plate type compressor shown in FIG. 2, taken along line IV-IV.

FIG. 4 is a sectional view of a swash plate type compressor according to a second embodiment of the present invention.

FIG. 5 is a sectional view of the swash plate type compressor shown in FIG. 4, taken along line VI-VI.

FIG. 6 is a longitudinal sectional view of a conventional swash plate type compressor.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Swash plate type compressor 2 Housing 3 Drive shaft 4 Swash plate 5 Piston 6 Shoe member 9a Balance member 13 Arm member 15 Crank chamber 19 Oil reservoir 20 Front housing 20a Oil passage 20g Oil receiving groove 25 First bolt 26 Second Bolt 50 Piston part 51 Rod part 52 Shoe receiving part 201b, 201b ′, 201b ″ First thrust trace 201c Second thrust trace 202 Shaft seal member 210 Shaft through hole

Claims (9)

[Claims] 1. A housing having a plurality of cylinder bores formed at an angular interval from each other about an axis, and a crank chamber adjacent to the cylinder bore, and extending on the axis and rotatably supported by the housing. A drive shaft, a swash plate mounted at an angle to the drive shaft and disposed in the crank chamber so as to rotate with the drive shaft, and slidably inserted into the plurality of cylinder bores, respectively. A plurality of pistons, and a member that converts the swinging motion of the swash plate into a linear reciprocating motion of the piston and transmits the same, and the housing includes a radial bearing that rotatably supports the drive shaft. A shaft through-hole, and an oil passage penetrating the crank chamber and the shaft through-hole. The rotation of the drive shaft lifts up the lubricating oil in the crank chamber. In a swash plate type compressor for supplying the lubricating oil through the oil passage to a bearing portion of the drive shaft,
A swash plate compressor, wherein an oil retaining means for receiving the lubricating oil is provided at an inlet of the oil passage. 2. The swash plate compressor according to claim 1, wherein
The housing includes a substantially cylindrical housing main body having the cylinder bore, and a substantially funnel-shaped front housing fixed to the housing main body so as to close one opening of the housing main body. Is connected to a rotor fixed to the drive shaft via a thrust needle bearing member, wherein the thrust needle bearing member has a first thrust trace that penetrates the drive shaft, and a thrust needle that penetrates the drive shaft. A second thrust trace held on the rotor side, and a bearing interposed between the first and second thrust traces, wherein the first thrust trace is provided on the crankcase side of the front housing. Is located so as to face the inner wall surface, and the inner wall surface extends radially from the drive shaft side. A large-diameter groove is formed, and further, on the inner wall surface of the front housing, a radially long oil receiving groove is formed at a part of the large-diameter groove. A swash plate type compressor, wherein one inlet of an oil passage is located. 3. The swash plate compressor according to claim 2, wherein
The swash plate compressor, wherein the oil retaining means is constituted by a part of the first thrust trace and the oil receiving groove. 4. The swash plate compressor according to claim 2, wherein
The swash plate compressor according to claim 1, wherein the oil retaining means is formed by radially extending a part of the first thrust trace. 5. The swash plate compressor according to claim 2, wherein
A plurality of lace bent portions bent toward the bottom surface of the large-diameter groove are formed on the periphery of the first thrust trace, and each of the lace bent portions is formed on the bottom surface of the large-diameter groove. Is formed, and the first thrust trace is prevented from rotating by fitting the race bent portion into the fitting hole. Swash plate compressor. 6. The swash plate type compressor according to claim 5, wherein
The width of the lace bend is smaller than the diameter of the fitting hole, and the dimension of the lace bend from the plate surface to the tip of the first thrust trace is the depth of the fitting hole. A swash plate compressor characterized in that the size is smaller than the size. 7. The swash plate compressor according to claim 2, wherein
The rotor has a balance member on a side opposite to a portion where the swash plate is connected, and the oil reservoir is made to have a size equal to an outer diameter of the balance member or larger than the balance member. A swash plate type compressor characterized by the above-mentioned. 8. The swash plate compressor according to claim 7, wherein
The swash plate type compressor, wherein the oil receiving groove is formed on a bottom surface of the large diameter groove. 9. A housing having a plurality of cylinder bores formed at an angular interval from each other around an axis, and a crank chamber adjacent to the cylinder bore, and extending on the axis and rotatably supported by the housing. A drive shaft, a swash plate mounted at an angle to the drive shaft and disposed in the crank chamber so as to rotate with the drive shaft, and slidably inserted into the plurality of cylinder bores, respectively. A plurality of single-headed pistons, and a shoe member slidably held by the single-headed piston and converting the oscillating motion of the swash plate into a linear reciprocating motion of the single-headed piston and transmitting the reciprocating motion. A shaft through hole with a radial bearing that rotatably supports the drive shaft,
An oil passage penetrating through the crank chamber and the shaft through-hole, wherein the rotation of the drive shaft lifts up the lubricating oil in the crank chamber, and the lubricating oil passes through the oil passage to a bearing portion of the drive shaft. A swash plate type compressor, wherein oil retaining means for receiving the lubricating oil is provided at an inlet of the oil passage.