JPH11294349A - Scroll compressor - Google Patents

Abstract

(57) [Problem] To provide a scroll compressor capable of preventing a large impact shear load from being applied to a limit pin when operation is stopped. A slide bush (2) is loosely fitted to a drive pin (1b) of a crankshaft (1), and a limit pin (20) is attached to the slide bush (2). The limit pin 20 is inserted through a restriction hole 1a of a flange portion 1c provided on the crankshaft 1 with a gap, and has a flange portion 20a at the tip. The difference (A1 + A2) between the diameter of the restriction hole 1a and the diameter of the limit pin 20 is set to be larger than the difference (B1 + B2) between the inner diameter of the cylindrical portion 2b of the slide bush 2 and the outer diameter of the drive pin 1c.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor.

[0002]

2. Description of the Related Art First, a scroll compressor disclosed in Japanese Patent Publication No. 2550704 will be described as a conventional scroll compressor.

FIG. 6 is a partial sectional view schematically showing the structure of a conventional scroll compressor. Referring to FIG. 6, a motor (not shown) and a compression element CF are mainly arranged in closed container 112.

[0004] A crankshaft 101 is provided so that a rotational force can be given by a motor. A drive pin 101b is provided at an eccentric position on the upper end of the crankshaft 101, and a counter weight 101a is provided on the opposite side of the drive pin 101b. A swing link 102 is attached to an upper end of the crankshaft 101.

The swing link 102 includes a drive pin 101
cylindrical part 102b fitted to bearing b through bearing cylinder 110
A regulating hole 102a provided on a surface facing the counterweight 101c; a cylindrical portion 102b;
And a central through-hole 102d provided between 2a.

The control hole 102a has a counter weight 1
The limit pin 120 attached to the reference numeral 01a is inserted. Here, there is a predetermined gap between the limit pin 120 and the restriction hole 102a, and the swing link 102 is arranged so as to be swingable by a predetermined angle around the drive pin 102b. That is, the limit pin 120 restricts the movement of the swing link 102 in the radial direction. Further, a flange 120a having a diameter larger than the diameter of the restriction hole 102a is provided on the head of the limit pin 120. The axial movement of the swing link 102 with respect to the crankshaft 101 is restricted by the collar 120a.

As described above, the limit pin 120 restricts the movement of the swing link 102 with respect to the crankshaft 101 both in the radial direction and the axial direction.

[0008] A compression element CF is provided to apply a rotational force of the crankshaft 101 via the swing link 102.

The compression element CF includes a movable scroll 103
And a fixed scroll 104. The movable scroll 103 has a head plate 103a, a spiral tooth part 103b protruding from the front surface of the head plate 103a, and a boss 103c protruding from the back surface of the head plate 103a. Boss 103
c is a central through hole 1 provided in the swing link 102.
01d via a bearing 105. The fixed scroll 104 includes a head plate 104a and the head plate 10a.
4a, and a spiral tooth portion 104b protruding from 4a.
The spiral tooth portion 104b meshes with the spiral tooth portion 103b of the movable scroll 103 to constitute a compression chamber.

[0010] The swing link 102 has a movable scroll 103 with a constant diameter relative to the fixed scroll 104 in order to absorb a machining error of the spiral tooth portions 103b and 104b and to ensure a smooth sliding operation. It is possible to freely move in the direction.

[0011]

In the conventional scroll compressor described above, each time the operation is stopped, the limit pin 1
20 has a problem that an impact shear load is applied.
Hereinafter, this will be described in detail.

During operation of the scroll compressor, the orbiting scroll 103 revolves orbiting due to the rotation of the crankshaft 101. Accordingly, the spiral tooth portions 103b, 10b of the movable scroll 103 and the fixed scroll 104
The compression chamber constituted by 4b moves from the outer peripheral side to the inner peripheral side while gradually reducing the volume. Therefore, the refrigerant gas in the outermost compression chamber is gradually compressed and reaches the innermost compression chamber, where it is discharged from the compression element CF through the discharge port 104c.

For this reason, when the operation of the scroll compressor is stopped, the pressure of the refrigerant gas is higher in the inner compression chamber than in the outer compression chamber. Therefore, the orbiting scroll 103 stops after rotating for several seconds so that the gas pressure in the compression chambers on the inner peripheral side and the outer peripheral side is equalized.

At this time, due to the inertial force due to the forward / reverse rotation, the swing link 102, as shown in FIG.
03b, 104b are in the radial direction opposite to the position where they are pressed against each other (as shown in FIG. 8, the spiral tooth portions 103b,
104b are separated from each other). This position is usually a position where the swing link 102 is restricted by the limit pin 120. That is, the swing link 102 hits the limit pin 120 each time the operation is stopped, and the limit pin 120 receives an impact shear load from the swing link 102, and is easily broken or dropped.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a scroll compressor which can prevent a large impact shear load from being applied to a limit pin when operation is stopped.

[0016]

According to a first aspect of the present invention, there is provided a scroll type compressor including a drive shaft, a slide bush, a movable scroll, and a limit pin. The drive shaft has a flange portion that extends to the outer peripheral side in the radial direction and has a through hole, and an eccentric pin portion provided at an end in the axial direction with respect to the collar portion. The slide bush is loosely fitted to the eccentric pin portion. The movable scroll has a bearing part that forms a sliding part with the outer peripheral surface of the slide bush. The limit pin is inserted into the through hole of the collar with a gap, and is attached to the slide bush. The movement of the slide bush in the radial direction with respect to the drive shaft is regulated by a gap between the outer diameter of the eccentric pin portion and the inner diameter of the slide bush, and the movement in the axial direction is regulated by a limit pin attached to the slide bush.

In the scroll type compressor according to the first aspect, since the slide bush that is loosely fitted to the eccentric pin portion is used, the axial movement and the radial movement of the slide bush with respect to the crankshaft can be dispersed. it can. That is, the axial movement of the slide bush can be restricted by the limit pin, and the radial movement can be restricted by the eccentric pin portion. For this reason, even if the slide bush moves in the radial direction when the operation is stopped, the slide bush does not stop by hitting the limit pin, thereby preventing a large impact shear load from being applied to the limit pin. Therefore, it is possible to prevent the limit pin from being broken or removed.

Since the eccentric pin portion can be usually made thicker than the limit pin, it is possible to disregard the adverse effects of applying an impact shear load to the eccentric pin portion.

Further, since the axial movement of the slide bush can be restricted by merely attaching the limit pin, the number of parts can be reduced as compared with the case where the axial movement of the slide bush is restricted by a spring or a C-shaped retaining ring. .

Further, since the movement of the slide bush in the axial direction can be restricted by the limit pin, it is possible to prevent the slide bush from being inclined or raised with respect to the drive shaft during operation. Therefore, it is possible to prevent the occurrence of one-sided contact, abnormal noise and vibration on the sliding surface between the slide bush and the orbiting scroll, and to prevent the lubricating oil from the tip of the eccentric pin portion from sliding between the bearing portion and the slide bush. It can be smoothly supplied to the moving part.

In the scroll type compressor according to the present invention, the limit pin has a flange portion having a diameter larger than the diameter of the through hole on a side opposite to the slide bush with the flange portion of the drive shaft interposed therebetween. ing. The flange portion of the limit pin has a gap with the flange portion of the drive shaft. The limit pin restricts the axial movement of the slide bush to a predetermined amount or less by a gap between the flange portion of the limit pin and the flange portion of the drive shaft while allowing the slide bush to move in the radial direction with respect to the drive shaft. .

Thus, the restriction of the axial movement of the slide bush with respect to the drive shaft can be realized by the limit pin.

[0023] In the scroll compressor according to the third aspect, the slide bush has a balance weight for balancing the rotating system when the drive shaft rotates.

Thus, the centrifugal force generated by the orbital motion of the movable scroll can be offset by the centrifugal force generated by the balance weight. Therefore, it is possible to suppress the contact pressure between the spiral tooth portions of the scroll from becoming excessive, and to prevent the spiral tooth portion from being damaged.

In the scroll type compressor according to the present invention, the difference between the diameter of the through hole in the flange of the drive shaft and the diameter of the limit pin is larger than the difference between the outer diameter of the eccentric pin and the inner diameter of the slide bush. .

By adjusting the gap in this manner, the radial movement of the slide bush with respect to the drive shaft can be restricted by the gap between the outer diameter of the eccentric pin portion and the inner diameter of the slide bush.

[0027]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a partial sectional view schematically showing a configuration of a scroll compressor according to an embodiment of the present invention. FIG. 2 is an enlarged partial cross-sectional view showing the configuration near the slide bush loosely fitted to the drive pin 1b in FIG. 1, and FIG. 3 is a schematic cross-sectional view along the line II in FIG.

Referring mainly to FIG. 1, a motor M and a compression element CF are mainly disposed in the sealed container 12.

The motor M has a stator 8 fixed to the inner wall of the closed casing 12, and a rotor 9 facing the stator 8 at a predetermined interval. The crankshaft 1 is connected to the rotor 9. The crankshaft 1 has a flange 1c, a drive pin 1b, and a restriction hole 1a. The restriction hole 1a is provided in the collar 1c. The drive pin 1b is located closer to the axial end of the crankshaft 1 than the collar 1c, and is provided eccentrically with respect to the crankshaft 1. The slide bush 2 is loosely fitted to the drive pin 1b.

The slide bush 2 has a cylindrical portion 2b, a flange portion 2c, a balance weight 2d, and a hole 2a. The cylindrical portion 2b is fitted with a gap between the outer peripheral surface of the drive pin 1b and the balance weight 2d.
Is mounted on the outer peripheral surface of the lower end of the drive pin 1b in a direction opposite to the eccentric direction of the drive pin 1b. The collar 2c is
It is attached to the outer peripheral surface of the lower end portion of b, at least on the opposite side to the balance weight 2d. The hole 2a is
It is provided on the lower end surface of the balance weight 2d at a position exposed from the restriction hole 1a. The limit pin 20 is engaged with the hole 2a.

The limit pin 20 is inserted through the restriction hole 1a with a gap. The head of the limit pin 20 has a flange 20a having a diameter larger than the diameter of the restriction hole 1a.
Is provided.

The lower end surfaces of the flange 2c of the slide bush 2 and the balance weight 2d are connected to the flange 1 of the crankshaft 1.
c can be in contact with the upper end surface.

The crankshaft 1 includes a rolling bearing 7 provided on an upper housing 6 and a lower housing (not shown).
And is supported by a bearing (not shown).

A compression element CF is provided so that rotational force can be applied from the drive pin 1b of the crankshaft 1 via the slide bush 2.

The compression element CF has a movable scroll 3 and a fixed scroll 4. The movable scroll 3
End plate 3a, spiral tooth portion 3b projecting from the front surface of end plate 3a
And a boss 3c protruding from the back surface of the end plate 3a. The drive pin 1b and the cylindrical portion 2b of the slide bush 2 are received in the boss 3c. Further, a slide bearing 5 constituting a sliding portion with the outer peripheral surface of the cylindrical portion 2b is mounted on the inner peripheral surface of the boss portion 3c. The movable scroll 3 is supported by an Oldham coupling so as to revolve while receiving its rotational force from the crankshaft 1 while keeping its attitude relatively. The fixed scroll 4 includes a head plate 4a.
And a spiral tooth 4b protruding from the end plate 4a. The spiral teeth 4b mesh with the spiral teeth 3b of the orbiting scroll 3 to form a compression chamber. The fixed scroll 4 is fastened and fixed to the upper housing 6 by, for example, a bolt.

The upper housing 6 and the lower housing (not shown) are fixed to each other in a closed container 12. Further, the closed container 12 is provided with a suction pipe 10 for sucking the refrigerant gas from the outside to the inside, and a discharge pipe 11 for discharging the refrigerant gas from the inside to the outside.

Referring mainly to FIG. 2, a gap C between the flange 20a of the limit pin 20 and the flange 1c of the crankshaft 1 will be described.
Is configured to be smaller than the gap D between the upper end surface of the slide bush 2 and the bottom surface of the boss 3c.

Referring mainly to FIG. 3, the difference (A1 + A2) between the diameter of the restriction hole 1a and the diameter of the limit pin 20 is the difference between the inner diameter of the cylindrical portion 2b of the slide bush 2 and the outer diameter of the drive pin 1c. It is configured to be larger than (B1 + B2).

Since each dimension is set as described above,
The movement of the slide bush 2 in the radial direction with respect to the crankshaft 1 is restricted by a gap between the outer diameter of the drive pin 1c and the inner diameter of the cylindrical portion 2b of the slide bush 2. Further, the movement of the slide bush 2 in the axial direction with respect to the crankshaft 1 is restricted by a limit pin 20 attached to the slide bush 2.

In the scroll compressor according to the present embodiment,
Each time the operation is stopped, an impact shear load is prevented from being applied to the limit pin 20. Hereinafter, this will be described.

In this embodiment, the slide bush 2 is used and the dimensions of the respective parts are set as described above, so that the movement of the slide bush 2 in the radial direction and the axial direction is restricted by the drive pin 1c and the limit pin. 20 and can be dispersed. For this reason, even when the slide bush 2 moves relative to the crankshaft 1 as shown in FIGS. 4 and 5 due to the reverse rotation of the movable scroll 3 when the operation of the scroll compressor is stopped, the slide bush 2 remains Before hitting 20, it hits the drive pin 1b and stops. That is, the limit pin 20 does not receive the impact shear load from the slide bush 2 at the time of reverse rotation when the operation of the scroll compressor is stopped. Therefore, the limit pin 20 does not break or fall out due to the impact shear load.

In this case, the impact shear load is applied to the drive pin 1b.
Can be generally thicker than the limit pin 20. For this reason, the adverse effects (for example, breakage of the drive pin 1b) due to the impact shear load applied to the drive pin 1b can be ignored.

The crankshaft 1 of the slide bush 2
Is restricted by the limit pin 20, the inclination of the slide bush 2 with respect to the crankshaft 1 due to the load fluctuation during operation, that is, the slide bush 2 is prevented from fluttering. For this reason, it is possible to prevent the sliding surface between the outer peripheral surface of the slide bush 2 and the sliding bearing 5 from hitting one side, and to prevent occurrence of abnormal noise or vibration.

Further, the slide bearing 5 and the slide bush 2
The supply of the lubricating oil to the sliding surface is performed from the supply passage 1d in FIG. For this reason, when the slide bush 2 rises in the figure with respect to the crankshaft 1, the path of the lubricating oil is blocked. However, in this embodiment, since the movement of the swing link 2 in the axial direction is restricted by the limit pin 20, the lubricating oil path can be supplied smoothly without blocking the path of the lubricating oil.

Further, since the axial movement of the slide bush 2 can be restricted by merely attaching the limit pin 20, the number of parts can be reduced as compared with the case where the axial movement of the slide bush is restricted by a spring or a C-shaped retaining ring. Can be.

When the movement of the swing link 102 in both the radial direction and the axial direction is restricted by the limit pin 120 as in the conventional example shown in FIG.

The limit pin 120 is connected to the movable scroll 10
3, the movement of the swing link 102 must be stopped at the time of the stop after the reverse rotation, but at the time of restart, the spiral tooth 103
The movement until the b and 104b come into contact with each other must not be restricted. If the radial gap between the spiral teeth 103b and 104b is too large at the position regulated by the limit pin 120 at the time of stopping, poor pressing of the spiral teeth 103b and 104b occurs at the time of restart. . From the above, if the limit pin 120 is to perform the regulation of the radial movement of the swing link 102, the required positional accuracy of the limit pin 120 and the regulation hole 102a located at a position eccentric from the center of the crankshaft 101 by a considerable amount is reduced. Will be expensive.

On the other hand, also in the present embodiment, since the limit pin 20 is located at a position eccentric with respect to the drive pin 1b, severe processing accuracy is required to maintain the position accuracy. However, since the limit pin 20 does not restrict the radial movement of the slide bush 2, a stricter machining accuracy than the conventional example is not required.

Since the direction in which the limit pin 20 is pressed into the balance weight 2d is directed upward in the figure, the balance weight of the balance weight 2d does not decrease due to the mounting of the limit pin 20.

The embodiments disclosed this time are to be considered in all respects as illustrative and not restrictive. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

[0052]

According to the scroll compressor of the first aspect, since the slide bush that is loosely fitted to the eccentric pin is used, the axial movement and the radial movement of the slide bush with respect to the crankshaft are dispersed. be able to. That is, the axial movement of the slide bush can be restricted by the limit pin, and the radial movement can be restricted by the eccentric pin portion. For this reason, even if the slide bush moves in the radial direction when the operation is stopped, the slide bush does not stop by hitting the limit pin, thereby preventing a large impact shear load from being applied to the limit pin. Therefore, it is possible to prevent the limit pin from being broken or removed.

Since the eccentric pin portion can be generally made thicker than the limit pin, it is possible to ignore the adverse effects caused by the impact shear load applied to the eccentric pin portion.

Further, since the axial movement of the slide bush can be restricted only by attaching the limit pin, the number of parts can be reduced as compared with the case where the axial movement of the slide bush is restricted by a spring or a C-shaped retaining ring. .

Further, since the movement of the slide bush in the axial direction can be restricted by the limit pin, it is possible to prevent the slide bush from being inclined or raised relative to the drive shaft during operation. For this reason, it is possible to prevent the occurrence of one-sided contact on the sliding surface between the slide bush and the orbiting scroll, the occurrence of abnormal noise and vibration, and to prevent the lubricating oil that has come out from the tip of the eccentric pin portion from flowing between the bearing portion and the slide bush. It can be smoothly supplied to the sliding part.

In the scroll compressor according to the second aspect, the limit pin has a flange portion having a diameter larger than the diameter of the through hole on a side opposite to the slide bush with the collar portion of the drive shaft interposed therebetween. ing. The flange portion of the limit pin has a gap with the flange portion of the drive shaft. The limit pin restricts the axial movement of the slide bush to a predetermined amount or less by a gap between the flange portion of the limit pin and the flange portion of the drive shaft while allowing the slide bush to move in the radial direction with respect to the drive shaft. .

Thus, the axial movement of the slide bush with respect to the drive shaft can be restricted by the limit pin.

In the scroll compressor according to the third aspect, the slide bush has a balance weight for balancing the slide bush when the drive shaft rotates.

Thus, the centrifugal force generated by the orbital motion of the orbiting scroll can be offset by the centrifugal force generated by the balance weight. Therefore, it is possible to suppress the contact pressure between the spiral tooth portions of the scroll from becoming excessive, and to prevent the spiral tooth portion from being damaged.

In the scroll compressor according to the fourth aspect, the difference between the diameter of the through hole in the flange of the drive shaft and the diameter of the limit pin is larger than the difference between the outer diameter of the eccentric pin and the inner diameter of the slide bush. .

By adjusting the gap as described above, the movement of the slide bush in the radial direction with respect to the drive shaft can be restricted by the gap between the outer diameter of the eccentric pin portion and the inner diameter of the slide bush.

[Brief description of the drawings]

FIG. 1 is a sectional view partially showing a configuration of a scroll compressor according to an embodiment of the present invention.

FIG. 2 is an enlarged cross-sectional view showing a configuration near a slide bush in FIG. 1;

FIG. 3 is a schematic sectional view taken along line II of FIG. 2;

4 is a cross-sectional view corresponding to FIG. 2, showing a state in which a slide bush has moved in a radial direction with respect to a crankshaft.

5 is a cross-sectional view corresponding to FIG. 3, showing a state in which a slide bush has moved in a radial direction with respect to a crankshaft.

FIG. 6 is a cross-sectional view partially showing a configuration of a conventional scroll compressor.

FIG. 7 is a partial cross-sectional view showing a state where spiral tooth portions are in contact with each other.

FIG. 8 is a partial cross-sectional view showing a state where spiral tooth parts are separated from each other.

[Explanation of symbols]

 Reference Signs List 1 crankshaft 1a regulating hole 1b drive pin 1c collar 2 slide bush 2a hole 2b cylinder 2c collar 2d balance weight 3 movable scroll 3c boss 4 fixed scroll 5 sliding bearing 20 limit pin CF compression element

Claims (4)

[Claims] A diametrically extending outer peripheral side and a through hole (1).
a) a drive shaft (1) having a collar portion (1c) having an a), an eccentric pin portion (1b) provided at an axial end portion relative to the collar portion (1c), and the eccentric pin portion (1b). A movable scroll (3) having a bearing (5) constituting a sliding portion between a slide bush (2) loosely fitted on the outer peripheral surface of the slide bush (2).
And a limit pin (20) inserted through the through hole (1a) of the collar portion (1c) with a gap and attached to the slide bush (2), and the driving of the slide bush (2) is provided. The control of the movement in the radial direction with respect to the shaft (1) is performed by the eccentric pin (1b).
A scroll type compression having a configuration in which a gap between an outer diameter and an inner diameter of the slide bush (2) is used, and the movement in the axial direction is restricted by the limit pin (20) attached to the slide bush (2). Machine. 2. The diameter of the limit pin (20) being larger than the diameter of the through hole (1a) on the opposite side of the slide bush (2) across the collar (1c) of the drive shaft (1). And a gap (C) between the collar (20a) of the limit pin (20) and the collar (1c) of the drive shaft (1). The limit pin (20) allows the slide bush (2) to move in the radial direction with respect to the drive shaft (1) while allowing the flange (20) of the limit pin (20) to move.
The axial movement of the slide bush (2) is restricted to a predetermined amount or less by the gap (C) between a) and the collar portion (1c) of the drive shaft (1). The scroll-type compressor as described. 3. The balance bush (2) for balancing the slide bush (2) when the drive shaft (1) rotates.
The scroll compressor according to claim 1, comprising d). 4. The collar (1c) of the drive shaft (1).
The diameter of the through hole (1a) and the limit pin (20)
Difference (A1 + A2) from the diameter of the eccentric pin (1b)
The difference between the outer diameter and the inner diameter of the slide bush (2) (B1 +
The scroll compressor according to claim 1, which is larger than B2).