JPH0444862Y2 - - Google Patents

Description

[Detailed Description of the Invention] Purpose of the Invention (Field of Industrial Application) The present invention relates to a compressor in which a piston is reciprocated via a roller using a three-dimensional cam, and specifically relates to a support structure for the roller.

(Prior Art) In this type of cam compressor, as shown in FIGS. 4 to 6, a pair of heads 52 are installed in a neck 53 in a cylinder bore formed in a cylinder block (not shown).
At the same time, a three-dimensional cam 55 is attached to the drive shaft 54 inserted into the shaft hole of the cylinder block, and the piston 5
A cylindrical mooring recess 5 provided with 1 in its head 52.
It is moored to the three-dimensional cam 55 so as to be able to reciprocate through a roller 56 fitted into the roller 2a (Japanese Patent Application Laid-open No. 57-1999).
110783).

Here, in order to enable smooth reciprocation of the piston 51, as shown in FIG.
A gap C ₁ is provided between the roller 56 and the outer periphery of the three-dimensional cam 55, and a gap (roller clearance) C ₂ is provided between the roller 56 and the cam surface of the three-dimensional cam 55, as shown in FIG.

(Problem to be solved by the invention) However, in the above compressor, the piston 51
There was a problem that the rolling of the drum produced a hitting sound, which caused a lot of noise.

That is, the roller 56 on the compression stroke side is moved by the three-dimensional cam 55 due to the load applied to the head 52 of the piston 51.
It works to maintain the optimal contact position. At this time, the piston 51 rolls as shown by the arrow at the top of FIG. 6 due to the existence of the gap _C1 .

At this time, since the roller 56 on the suction stroke side has the roller clearance _C2 , the piston 5
It detaches from the mooring recess 52a of No. 1 and falls down diagonally,
It intermittently bites into the mooring recess 52a to generate a tapping sound. Furthermore, since the cam surface of the three-dimensional cam 55 is a curved surface, when the roller 56 is tilted, the contact position between the roller 56 and the three-dimensional cam 55 changes, and the roller 56 bites into the three-dimensional cam 55 like a wedge. It wakes up and makes a banging sound.

Furthermore, in the past, the roller clearance _C2 was adjusted by selective fitting, which required considerable effort and time.

Structure of the Invention (Means for Solving the Problems) Therefore, in order to solve the above-mentioned problems, the compressor of the invention has a pair of heads connected by a neck within a cylinder bore formed in a cylinder block. At the same time as the piston is fitted, a three-dimensional cam is attached to the drive shaft inserted into the shaft hole of the cylinder block, and the three-dimensional cam is attached to the three-dimensional cam through a roller that fits into a cylindrical mooring recess provided in the head of the piston. In a compressor moored so as to be reciprocally movable, a radius of curvature larger than a radius of the roller and a latch part that is permanently latched to both edges of the mooring recess is provided between the mooring recess of the piston and the roller. We took a measure of interposing a leaf spring consisting of a biasing section and a biasing section.

(Operation) The roller on the compression stroke side (high load side) is pressed against the three-dimensional cam by the load applied to the head of the piston, and works to maintain the optimum contact position. At this time,
The piston attempts to roll, but the elastic force stored in the biasing portion of the leaf spring presses the piston, suppressing the rolling. Here, since the biasing portion of the leaf spring has a radius of curvature larger than the radius of the roller, it can exert an effective elastic force on the roller. Furthermore, since the hooking portions of the leaf spring are permanently hooked to both edges of the mooring recess, the leaf spring will not rattle or come off.

On the other hand, the roller on the suction stroke side (low load side) is pressed against the three-dimensional cam by a leaf spring, acting in a direction to reduce or eliminate the roller clearance. Furthermore, the roller can have a degree of freedom within the mooring recess due to the expansion and contraction of the leaf spring and the gap between the mooring recess of the piston and the leaf spring. Therefore, even if excessive rolling occurs in the piston, the piston will not come off the mooring recess or fall down obliquely, and the piston will maintain an appropriate contact position with respect to the three-dimensional cam.

(Example) Hereinafter, an example embodying the present invention will be described with reference to FIGS. 1 to 3.

First, according to Figure 3, 5 cylinders on each side, that is, a total of
To explain a 10-cylinder cam type compressor, both edges of cylinder blocks 1 and 2, which are opposed to each other in the front and rear, are closed by front and rear housings 5 and 6 via front and rear valve plates 3 and 4. are connected by an appropriate number of bolts 7 inserted through bolt insertion holes 1a and 2a. A cam chamber 8 is formed at the junction of the cylinder blocks 1 and 2, and a three-dimensional cam is fixed to the drive shaft 9 passing through shaft holes 1b and 2b formed in the center of both cylinder blocks 1 and 2. 10 are accommodated.

Five pairs of cylinder bores 11 are bored in the cylinder blocks 1 and 2 in parallel with the drive shaft 9 and at radial positions centered on the drive shaft 9, and each cylinder bore 11 has a pair of heads 13 at the neck. A double-headed piston 12 connected by 14 is inserted. These pistons 12 are cylindrical rollers 15
It is moored to the three-dimensional cam 10 via the three-dimensional cam 10, and can reciprocate within the cylinder bore 11 by the rotational force of the three-dimensional cam 10.

That is, as shown in FIGS. 1 and 2, cylindrical mooring recesses 13 for supporting the rollers 15 are provided on the inner facing surfaces of the heads 13 on both sides of each piston 12.
A is formed between the mooring recess 13a and the roller 15, and a bent hook portion 17 that is permanently engaged with both edges of the mooring recess 13a, and a curved hook portion 17 having a radius larger than the radius of the roller 15. Curved biasing part 1 with radius
A plate spring 16 consisting of 8 is interposed. Moreover, the distance between both mooring recesses 13a is (3-dimensional cam 10
thickness) + 2 x (diameter of roller 15) + 2 x (plate spring 1
6 thickness) + (roller clearance), and the plate spring 16 and the mooring recess 13a
A gap remains between them, and each leaf spring 16 presses the roller 15 against the cam surface of the three-dimensional cam 10.

Note that in order to enable smooth reciprocation of the piston 12, a gap is provided between the abdomen 14a formed in the neck 14 of the piston 12 and the outer periphery of the three-dimensional cam 10.

The front and rear housings 5 and 6 have suction chambers 21 and 22 formed on their outer circumferential sides, respectively, and discharge chambers 23 and 24 formed on their center sides. Also,
The front and rear valve plates 3, 4 have suction ports 25, 26 for sucking refrigerant gas from suction chambers 21, 22 into each cylinder bore 11, respectively, and compressed refrigerant gas from each cylinder bore 11 to discharge chambers 23, 24. Discharge ports 27 and 28 for discharging are provided. Furthermore, suction valve mechanisms 29 and 3 are provided on the cylinder block 1 and 2 sides of the valve plates 3 and 4.
0 is provided, and discharge valve mechanisms 31 and 32 are provided on the housing 5 and 6 sides of the valve plates 3 and 4.

Next, the effects of the embodiment configured as described above will be explained.

Now, when the three-dimensional cam 10 is rotated by the rotation of the drive shaft 9, the piston 12 is reciprocated in the left-right direction in FIG. 3 within the cylinder bore 11 via the roller 15, and suction, compression, and discharge are performed.

Here, the roller 15 on the compression stroke side (high load side)
is pressed against the three-dimensional cam 10 by the load applied to the head 13 of the piston 12, and works to maintain the optimum contact position. At this time, the piston 12 tries to roll as explained in FIG. 6, but the piston 12 is pressed by the elastic force stored in the biasing part 18 of the leaf spring 16, and the rolling is suppressed. . Here, the biasing portion 18 of the leaf spring 16
has a radius of curvature larger than the radius of the roller 15, so that it can exert an effective elastic force on the roller 15. Furthermore, the latching portion 17 of the leaf spring 16 is connected to the mooring recess 1
Since the leaf spring 16 is permanently hooked to both edges of the leaf spring 3a, the leaf spring 16 will not rattle or come off.

On the other hand, the roller 15 on the suction stroke side (low load side) is also pressed against the three-dimensional cam 10 by the leaf spring 16, acting in a direction to reduce or eliminate the roller clearance. Furthermore, due to the expansion and contraction of the leaf spring 16 and the gap between the mooring recess 13a of the piston 12 and the leaf spring 16, the roller 15 can have a degree of freedom within the mooring recess 13a. Therefore, even if excessive rolling occurs in the piston 12, the piston 12 will not come off the mooring recess 13a or fall down diagonally, and will act to maintain an appropriate contact position with the three-dimensional cam 10. .
Therefore, the piston 12 does not bite against the mooring recess 13a or the three-dimensional cam 10, and no hitting noise is generated due to this biting, so that noise is reduced.

Furthermore, since the roller clearance is reduced or eliminated as described above, there is also the effect that clearance adjustment, which was conventionally performed by selective fitting, becomes unnecessary.

It should be noted that the present invention is not limited to the configuration of the above-mentioned embodiments, and may be modified and embodied as desired without departing from the spirit of the invention, for example, as described below.

(1) The biasing portion 18 of the leaf spring 16 may have a radius of curvature larger than the radius of the roller 15;
The biasing portion may have an infinite radius of curvature, that is, it may have a flat plate shape. Further, the radius of curvature may not be constant.

(2) The shape of the mooring recess 13a is not limited to a cylindrical surface.

Effects of the invention As detailed above, the present invention not only prevents roller biting and hammering noise caused by piston rolling and reduces noise, but also improves the clearance achieved by conventional selective fitting. This has the excellent effect of eliminating the need for adjustment.

[Brief explanation of drawings]

1 to 3 show an embodiment of a compressor embodying the present invention. The figure is a perspective view of a piston, FIG. 3 is a vertical cross-sectional view of the central part of the same compressor, FIGS. 4 to 6 show conventional examples of the compressor, and FIG. 4 is a partially cutaway cross-sectional view of important parts.
FIG. 5 is a perspective view of the piston, and FIG. 6 is a central cross-sectional view. 1, 2...Cylinder block, 1b, 2b...
Shaft hole, 9... Drive shaft, 10... Three-dimensional cam, 11...
... cylinder bore, 12 ... piston, 13 ... head, 14 ... neck, 15 ... roller, 16 ... leaf spring, 17 ... latching section, 18 ... biasing section.

Claims (1)

[Claim for Utility Model Registration] A piston consisting of a pair of heads connected by a neck is fitted into a cylinder bore formed in a cylinder block, and a three-dimensional cam is attached to a drive shaft inserted into the shaft hole of the cylinder block. and in a compressor in which the piston is moored reciprocally to the three-dimensional cam via a roller supported by a cylindrical mooring recess provided in the head thereof, between the mooring recess of the piston and the roller. teeth,
A compressor in which a leaf spring is interposed, which is composed of a hook part that is permanently hooked to both edges of the mooring recess, and a biasing part having a radius of curvature larger than the radius of the roller.