JP2001193649A - Reciprocating refrigerant compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent a liquefied refrigerant from leaking toward a suction chamber or the suction valve from deformation or breakage by enlarging the area of the suction port. SOLUTION: A suction port 15 is divided into a plurality of holes 15a, 15b, 15c by ribs 61a, 61b, 61c. For example in case a liquefied refrigerant is compressed in a compression chamber, an excessive load willing to deflect large the suction valve 21 toward the suction chamber will act on the suction valve 21, but because the suction valve 21 is supported by the ribs 61a, 61b, 61c, its 21 deflection remains little, and the suction port 15 is closed certainly.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a reciprocating type compressor used as a refrigerant compressor of an air conditioner for automobiles, and more particularly, to a reciprocating type compressor in which a piston reciprocates like a wobble plate type compressor or a swash plate type compressor. The present invention relates to a reciprocating refrigerant compressor.

[0002]

2. Description of the Related Art A wobble plate compressor includes a cylinder block having a plurality of cylinder bores, a plurality of pistons reciprocating in the cylinder bore, a cylinder head fixed to an end surface of the cylinder block via a valve plate, and a valve. A plurality of suction valves for opening and closing a plurality of suction ports formed in the plate.

[0003] A compression chamber is formed inside the cylinder bore, and the volume of the compression chamber changes as the piston moves.

In the cylinder head, there is formed a suction chamber for accommodating low-pressure refrigerant gas flowing from the evaporator side.

[0005] The number of suction valves and the number of suction ports of the valve plate are each equal to the number of cylinder bores, similarly to the number of compression chambers and the number of pistons.

[0006] The suction chamber communicates with the compression chamber via a suction port.

In the suction stroke, as the volume of the compression chamber gradually increases, the suction valve flexes toward the compression chamber to open the suction port, and the refrigerant gas in the suction chamber is sucked into the compression chamber via this suction port.

FIG. 12 is a partially enlarged plan view of a valve plate of a conventional rocking plate compressor.

The valve plate 702 has a suction port 71.
5, and a discharge port 716 is formed inside the suction port 715 (in the radial direction inside the valve plate 702). Further, the suction port 715 and the discharge port 716 are respectively provided at the opening edges 70 of the cylinder bore.
6a. A hole 763 is formed in the suction valve 721 so that the discharge port 716 is not closed by the suction valve 721.

An opening edge 706a of the cylinder bore,
A recess 770 for stopper is formed at a position facing the tip 721a of the suction valve 721.

As the piston moves to the bottom dead center during the suction stroke, a large pressure difference is generated between the compression chamber and the suction chamber, and the suction valve 721 flexes toward the compression chamber and the suction port 715
Is opened, and the refrigerant gas in the suction chamber is sucked into the compression chamber via the suction port 715. At this time, the tip 721a of the suction valve 721 hits the stopper recess 770, and the amount of deflection thereof is limited.

The suction pulsation is reduced by reducing the depth dimension of the stopper recess 770 (the length from the end surface of the cylinder block to the bottom surface of the stopper recess 770).

As the piston moves to the top dead center during the compression stroke, the volume of the compression chamber gradually decreases, and the pressure in the compression chamber increases. At this time, the suction valve 721 is in close contact with the valve plate 702 at a high pressure, and blocks the suction port 715.

[0014]

However, when the depth of the stopper recess 770 is reduced, the suction efficiency is reduced and the performance of the refrigerant compressor is reduced.

In order to improve the performance of the refrigerant compressor, it is necessary to increase the opening area at the time of suction, and for that purpose, the area of the suction port 715 must be increased. If the area of the suction port 715 is increased, it is necessary to increase the size of the suction valve 721 accordingly.

However, when the area of the suction port 715 is increased, an excessive load is applied to the suction valve 721 during the so-called liquid compression in which the liquid (liquid refrigerant) is compressed in the compression chamber, and the liquid leaks to the suction chamber. Then, the suction valve 721 may be deformed or broken.

The present invention has been made in view of such circumstances, and its object is to increase the area of the suction port and to prevent leakage of liquid to the suction chamber side and deformation / damage of the suction valve. It is an object of the present invention to provide a reciprocating refrigerant compressor which can prevent the reciprocation.

[0018]

According to a first aspect of the present invention, there is provided a reciprocating refrigerant compressor comprising: a cylinder block having a plurality of cylinder bores; and a cylinder block fixed to an end face of the cylinder block via a valve plate. Cylinder head, a low-pressure chamber formed in the cylinder head, a plurality of suction ports provided in the valve plate for communicating the low-pressure chamber and the cylinder bore, and a plurality of opening and closing the plurality of suction ports. Wherein the number of the suction ports and the number of the suction valves are both equal to the number of the cylinder bores, wherein the suction ports are divided into a plurality of holes by ribs. Features.

For example, when the liquid is compressed in the compression chamber, an excessive load is applied to the suction valve during the compression stroke, and the suction valve is largely bent toward the suction chamber, but the suction valve is supported by the ribs. , Its excessive deflection is regulated.

A reciprocating refrigerant compressor according to a second aspect of the present invention is the reciprocating type refrigerant compressor according to the first aspect of the present invention, wherein the rib is formed substantially radially from a central axis of the cylinder bore. .

As described above, since the ribs are formed substantially radially from the central axis of the cylinder bore, the ribs do not have a large resistance to the refrigerant gas.

According to a third aspect of the present invention, there is provided a reciprocating refrigerant compressor according to the first or second aspect of the present invention, wherein a groove or a hole is formed in a surface of the rib.

Since the groove or the hole is formed on the surface of the rib as described above, the lubricating oil accumulated between the suction valve and the valve plate is discharged through the groove or the hole.

[0024]

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

FIG. 4 is a longitudinal sectional view showing a wobble plate compressor according to a first embodiment of the present invention, FIG. 1 is a perspective view showing a valve plate and a valve seat of the wobble plate compressor, and FIG. FIG. 3 is a plan view of the valve plate of FIG. 1, and FIG. 3 is a partially enlarged view of the valve plate of FIG.

A rear head (cylinder head) 3 is fixed to one end face of a cylinder block 1 of this compressor via a valve plate 2, and a front head 4 is fixed to the other end face.

The cylinder block 1 has a shaft 5
A plurality of cylinder bores 6 are disposed at predetermined intervals in the circumferential direction around the center. A piston 7 is slidably housed in the cylinder bore 6. A compression chamber 60 is formed inside the cylinder bore 6, and the volume of the compression chamber 60 changes as the piston 7 moves. At the position of the opening edge 6a of the cylinder bore 6 facing the tip 21a of the suction valve 21,
A stopper recess 70 is formed to regulate the bending of the distal end portion 21a of the suction valve 21 during suction (see FIGS. 2 and 3). The amount of deflection (opening) of the suction valve 21 is limited by the stopper recess 70.

A crank chamber 8 is provided in the front head 4.
A rocking plate 1 that swings around a hinge ball 9 in conjunction with the rotation of the shaft 5 is formed in the crank chamber 8.
0 is stored.

In the rear head 3, a discharge chamber 12 is provided.
A suction chamber 13 located around the discharge chamber 12 is formed.

The valve plate 2 has a plurality of discharge ports 16 for communicating the cylinder bore 6 with the discharge chamber 12.
And a plurality of suction ports 15 for communicating the cylinder bore 6 with the suction chamber 13 are provided at predetermined intervals in the circumferential direction. The discharge port 16 is opened and closed by a discharge valve 17,
The discharge valve 17 is fixed to an end face on the rear head side of the valve plate 2 with a rivet 19 together with a valve retainer 18. The suction port 15 is opened and closed by a suction valve 21, and the suction valve 21 is disposed between the valve plate 2 and the cylinder block 1. The discharge chamber 12 and the crank chamber 8 communicate with each other via a passage 79 and an orifice 80.

Suction valve 21, discharge valve 17, suction port 1
5, the number of discharge ports 16 and the number of compression chambers 60 are each equal to the number of cylinder bores 6 (five in this embodiment).

As shown in FIGS. 1 and 2, the suction port 1
The discharge port 5 and the discharge port 16 are respectively located inside the opening edge 6 a of the cylinder bore 6. The suction port 15 is located outside the discharge port 16 (outside the valve plate 2 in the radial direction).
Located in. Each of the five suction ports 15 is constituted by a plurality of holes 15a, 15b, 15c, and 15d. That is, one suction port 15 is constituted by the holes 15a, 15b, 15c, and 15d. One suction port 15
Are larger than the area of the suction port 315 of the conventional example (see FIGS. 3 and 12). At the same time, the distal end 21a of the suction valve 21 is changed to the distal end 721a of the conventional suction valve 721.
Is bigger than.

The holes 15a and 15d are substantially semicircular, and the holes 15b and 15c are substantially fan-shaped. Holes 15a, 15b,
15 c and 15 d are arranged along the opening edge 6 a of the cylinder bore 6. The holes 15a and 15b, the holes 15b and 15c, and the holes 15c and 15d are respectively formed with ribs 61a and 61d.
b, 61c.

As shown in FIG. 1, the five suction valves 21 are formed integrally with one valve seat 62. Each suction valve 2
A hole 63 is formed in 1 so that the discharge port 16 is not closed by the suction valve 21.

The cylinder block 1 is provided with a communication passage 31 for communicating the suction chamber 13 with the crank chamber 8, and a pressure regulating valve 32 is provided in the middle of the communication passage 31. Pressure adjustment between the inside of the cylinder 13 and the inside of the crank chamber 8 is performed.

The front end of the shaft 5 is formed by a radial bearing 26 in the front head 4, and the rear end of the shaft 5 is formed by a radial bearing 24 and a thrust bearing 2.
5, each is rotatably supported. A thrust flange 40 is fixed to the shaft 5, and a drive hub 41 is attached to the shaft 5 via an axially movable hinge ball 9. The thrust flange 40 is supported on the inner wall of the front head 4 via a thrust bearing 33. A part of the thrust flange 40 and a part of the drive hub 41 are connected by a link mechanism 42,
The rotation of the shaft 5 is transmitted from the thrust flange 40 to the drive hub 41 through the link mechanism 42. The swing plate 10 is attached to the drive hub 41 via a radial bearing 27 and a thrust bearing 28 so as to be relatively rotatable. The swing plate 10 is connected to the piston 7 via a connecting rod 11.

A coil spring 44 as a destroke spring is interposed between the hinge ball 9 and the boss 40b of the thrust flange 40. The coil spring 44 attaches the hinge ball 9 to the cylinder block 1 side. Be inspired.

A fixed washer 45 is fixed to the shaft 5 on the cylinder block 1 side.
A plurality of curved springs 46 and coil springs 47 as stroke springs are interposed between the hinge ball 5 and the hinge ball 9 in series.
6 and 47, the hinge ball 9 becomes the thrust flange 4
It is urged to the 0 side.

Next, the operation of the wobble plate compressor will be described.

When the rotational power of the engine (not shown) is transmitted to the shaft 5, the thrust flange 40 and the drive hub 41 rotate together with the shaft 5, and the swing plate 10 swings about the hinge ball 9 with the rotation. This swinging motion is transmitted to the piston 7 via the connecting rod 11, and is converted into a linear reciprocating motion of the piston 7. When the piston 7 reciprocates in the cylinder bore 6, the volume of the compression chamber 60 changes, and the suction, compression, and discharge of the refrigerant gas are sequentially performed by this volume change, and the swing plate 10
High-pressure refrigerant gas having a capacity corresponding to the inclination angle of the gas is discharged.

When the heat load decreases and the pressure regulating valve 32 closes the communication passage 31 and the pressure in the crank chamber 8 increases, the inclination angle of the swing plate 10 decreases, and the stroke amount of the piston 7 decreases, thereby causing discharge. The capacity is reduced. In contrast,
When the heat load increases and the pressure regulating valve 32 opens the communication passage 31 and the pressure in the crank chamber 8 decreases, the inclination angle of the swing plate 10 increases, the stroke amount of the piston 7 increases, and the discharge capacity increases. I do.

In the suction stroke, a large pressure difference is generated between the compression chamber 60 and the suction chamber 13 as the piston 7 moves to the bottom dead center, and the suction valve 21 is bent toward the compression chamber 60 to open the suction port 15. The refrigerant gas in the suction chamber 13 is sucked into the compression chamber 60 through the suction port 15. As described above, the five suction ports 15 each have a plurality of holes 15a to 15a.
15d, the sum of the areas of the holes 15a to 15d forming one suction port 15 is equal to the suction port 31 of the conventional example.
5, the suction efficiency of the refrigerant gas is higher than in the conventional example, and the capacity of the refrigerant compressor is improved. Further, the refrigerant gas to be sucked is rectified (this point is the third point).
The same applies to the embodiment).

In the compression stroke, the volume of the compression chamber 60 gradually decreases as the piston 7 moves to the top dead center, and the pressure in the compression chamber 60 increases. At this time, the suction valve 21 closes the suction port 15 and the discharge valve 17 closes the discharge port 16. During the discharge stroke, the volume of the compression chamber 60 is minimized, and the pressure in the compression chamber 60 is maximized. Compression chamber 6
When a certain pressure difference occurs between the pressure chamber 0 and the discharge chamber 12, the discharge valve 17 bends toward the discharge chamber 60, and the discharge port 17 is opened. At this time, the suction valve 21 blocks the suction port 15. At this time, the suction valve 21 is operated at a high pressure to
To close the suction port 15.

Further, for example, when the liquid is compressed in the compression chamber 60, an excessive load acting on the suction valve 21
Is largely bent to the suction chamber 13 side.
Since 1 is supported by the ribs 61a, 61b, 61c, its bending is regulated, and the sealing property is also ensured.

According to the first embodiment, the suction port 1
Even if the area of 5 is increased, leakage of the liquid refrigerant to the suction chamber 13 side and deformation or breakage of the suction valve 21 can be prevented.

FIG. 5 is a partially enlarged plan view of a valve plate of a wobble plate compressor according to a second embodiment of the present invention.
The structure of this rocking plate compressor other than the valve plate is the first.
The description is omitted because it is the same as the embodiment.

In this embodiment, the valve plate 102
Five suction ports 115 each have three holes 115
a, 15b, and 115c. Hole 115a,
Each of 115b and 115c has a circular shape, and is easily processed. The areas of the holes 115a and 115c are substantially equal, and the area of the hole 115b is smaller than the area of the hole 115a. The holes 115a and 115b, the holes 115b and 115c, and the holes 115a and 115c
Adjacent via 161b and 161c.

According to the second embodiment, the same effects as those of the first embodiment can be obtained.

FIG. 6 is a partially enlarged plan view of a valve plate of a swinging plate compressor according to a third embodiment of the present invention.
The structure of this rocking plate compressor other than the valve plate is the first.
The description is omitted because it is the same as the embodiment.

In this embodiment, the valve plate 202
The five suction ports 215 each have three holes 215.
a, 215b and 215c. Hole 215
a and 215c are substantially semicircular. The hole 215b is substantially fan-shaped. Holes 215a, 215b, holes 215b, 215
c are adjacent to each other via the ribs 261a and 261b.

According to the third embodiment, the same effects as those of the first embodiment can be obtained.

It should be noted that any of the suction ports 15, 115,
215 also has a plurality of holes 15a to 15d, 115a to 115d, respectively.
115c, 215a to 215c, a plurality of holes are arranged along the opening edge 6a of the cylinder bore 6, and the sum of the areas of a plurality of holes constituting one suction port is one of the conventional examples. The fact that the area is larger (almost three times) than the area of the suction port 315 is common to any of the above-described embodiments.

FIG. 7 is a perspective view showing a valve plate and a valve seat of a swinging plate compressor according to a fourth embodiment of the present invention, and FIG. 8 is a plan view of the valve plate. The structure of the oscillating plate compressor other than the valve plate is the same as that of the first embodiment, and a description thereof will be omitted.

The valve plate 302 of this embodiment includes ribs 61a and 61b of the valve plate 2 of the first embodiment.
One straight groove (groove) 64 is provided in each of the first grooves 61c. That is, in the fourth embodiment and the first embodiment, the point that each suction port 15 is constituted by four holes 15a to 15d and the holes 15a and 15b, the holes 15b and 15c, and the holes 15c and 15d are respectively Ribs 61a, 61
b, 61c, which are common to the points adjacent thereto,
The difference is that linear grooves 64 are provided on the surfaces of 1a, 61b and 61c, respectively.

When the suction valve 21 is in close contact with the valve plate 2 and closes the suction port 15, the lubricating oil accumulated between the suction valve 21 and the valve plate 2 is discharged through the linear groove 64.

Therefore, when a certain pressure difference occurs between the compression chamber 60 and the suction chamber 13 during the suction stroke, the suction valve 21
Opens quickly. Incidentally, if there is no linear groove 64, the lubricating oil between the suction valve 21 and the valve plate 2 causes the suction valve 21 to be adsorbed on the ribs 61a, 61b, 61c, and the opening timing of the suction valve 21 in the suction stroke is delayed. , The inhalation efficiency may be deteriorated.

The straight grooves 64 are formed by ribs 61a, 61b,
Since it is provided only in 61c, the seating of the suction valve 21 with respect to the valve plate 2 due to the linear groove 64 does not decrease.

According to the fourth embodiment, the same effect as that of the first embodiment can be obtained, and the timing of opening the suction valve 21 during the suction stroke can be prevented from being delayed. And improve the performance of the refrigerant compressor.

FIG. 9 is a partially enlarged plan view of a valve plate of a swinging plate compressor according to a fifth embodiment of the present invention.
The structure of this rocking plate compressor other than the valve plate is the first.
The description is omitted because it is the same as the embodiment.

The valve plate 402 of this embodiment is provided with the ribs 61a and 61b of the valve plate 2 of the first embodiment.
A plurality of round holes (holes) 164 are linearly arranged in each of 61c. That is, the fifth embodiment is different from the fifth embodiment in that each suction port 15 is constituted by four holes 15a to 15d, and that the holes 15a, 15b, holes 15b, 15c, and
c, 15d are respectively connected to ribs 61a, 61b, 6
The first embodiment and the fourth embodiment are common to the first embodiment and the fourth embodiment in that the plurality of round holes 164 are provided instead of the grooves 64a, 64b, and 64c in each of the ribs 61a, 61b, and 61c. It differs from the first and fourth embodiments in that it is provided.

According to the fifth embodiment, the same effects as those of the fourth embodiment can be obtained.

FIG. 10 is a partially enlarged plan view of a valve plate of an oscillating plate compressor according to a sixth embodiment of the present invention. The structure of the oscillating plate compressor other than the valve plate is the same as that of the first embodiment, and a description thereof will be omitted.

The valve plate 502 of this embodiment is the same as the rib 161a, 161 of the valve plate 102 of the second embodiment.
61b and 161c are provided with two parallel linear grooves (grooves) 264a and 264b, respectively. That is, the sixth embodiment differs from the sixth embodiment in that each suction port 15 is constituted by three holes 115a to 115d,
15b, holes 115b and 115c, holes 115a and 115c
Are ribs 1161a, 161b, 161
The third embodiment is common to the third embodiment in that it is adjacent via c.
It differs from the second embodiment in that a plurality of straight grooves 264a, 264b are provided in each of the ribs 161a, 161b, 161c.

According to the sixth embodiment, the same effects as those of the fourth embodiment can be obtained.

FIG. 11 is a partially enlarged plan view of a valve plate of a swinging plate compressor according to a seventh embodiment of the present invention. The structure of the oscillating plate compressor other than the valve plate is the same as that of the first embodiment, and a description thereof will be omitted.

The valve plate 602 of this embodiment is the same as the rib 261a, 261 of the valve plate 202 of the third embodiment.
61b, substantially trapezoidal holes 364a and substantially triangular holes 364b are alternately arranged on a straight line.
That is, the seventh embodiment differs from the seventh embodiment in that each suction port 215 is constituted by three holes 215a to 215d.
5a and 215b and holes 215b and 215c are third points at points adjacent to each other via ribs 261a and 61b.
The third embodiment is common to the third embodiment in that trapezoidal holes 364a and substantially triangular holes 364b are alternately arranged on a straight line in each of the ribs 261a and 261b.

According to the seventh embodiment, the same effects as those of the fourth embodiment can be obtained.

In each of the above-described embodiments, linear grooves 64, 264a, 264b, round holes 164, and polygonal holes (trapezoidal holes 364a and triangular holes 364b) have been proposed as examples of grooves and holes. Instead of ribs 61a-61
Even if particles are sprayed on the surfaces of c, 161a to 161c, 261a, 261b to make the surface roughness of the rib rough, a function almost equivalent to that of a hole or groove can be obtained.

In each of the above embodiments, the swinging plate type compressor is described as an example of the reciprocating type refrigerant compressor. However, the application range of the present invention is not limited to this, and the swash plate type compressor and the like may be used. The present invention can also be applied to the reciprocating refrigerant compressor of (1).

[0070]

As described above, according to the reciprocating refrigerant compressor of the first aspect of the present invention, even if the area of the suction port is enlarged, leakage of the liquid refrigerant to the suction chamber side and deformation of the suction valve may occur.
Damage can be prevented.

According to the reciprocating refrigerant compressor of the second aspect of the present invention, in addition to the effect of the first aspect of the present invention, the rib does not have a large resistance to the refrigerant gas, so that the flow of the refrigerant gas becomes smooth.

According to the reciprocating refrigerant compressor of the third aspect of the invention, in addition to the effects of the first or second aspect of the invention, it is possible to prevent the opening timing of the suction valve from being delayed in the suction stroke.

[Brief description of the drawings]

FIG. 1 is a perspective view showing a valve plate and a valve seat of a wobble plate compressor according to a first embodiment of the present invention.

FIG. 2 is a plan view of the valve plate of FIG. 1;

FIG. 3 is a partially enlarged view of the valve plate of FIG. 2;

FIG. 4 is a longitudinal sectional view showing a wobble plate compressor according to the first embodiment of the present invention.

FIG. 5 is a partially enlarged plan view of a valve plate of a wobble plate compressor according to a second embodiment of the present invention.

FIG. 6 is a partially enlarged plan view of a valve plate of a wobble plate compressor according to a third embodiment of the present invention.

FIG. 7 is a perspective view showing a valve plate and a valve seat of a swinging plate compressor according to a fourth embodiment of the present invention.

FIG. 8 is a plan view of the valve plate.

FIG. 9 is a partially enlarged plan view of a valve plate of a wobble plate compressor according to a fifth embodiment of the present invention.

FIG. 10 is a partially enlarged plan view of a valve plate of an oscillating plate compressor according to a sixth embodiment of the present invention.

FIG. 11 is a partially enlarged plan view of a valve plate of an oscillating plate compressor according to a seventh embodiment of the present invention.

FIG. 12 is a partially enlarged plan view of a valve plate of a conventional swinging plate compressor.

[Explanation of symbols]

1 Cylinder block 2, 102, 202, 302, 402, 502, 60
2,702 Valve plate 4 Rear head (cylinder head) 6 Cylinder bore 6a Opening edge 13 Suction chamber (low pressure chamber) 15,115,215 Suction port 15a, 15b, 15c, 15d, 115a, 115
b, 115c, 215a, 215b, 215c Hole 21 Suction valve 61a, 61b, 61c, 161a, 161b, 161
c, 261a, 261b rib

 ────────────────────────────────────────────────── ─── Continuing from the front page (72) Inventor Katsumi Sakamoto 39, Higashihara, Chiyo, Odai-gun, Osato-gun, Saitama Prefecture F term (reference) 3H003 AA03 AB07 AC03 BC04 CA00 CB01 CB07 CC11 CD02 CD03 CD04 CE04 CE05

Claims (3)

[Claims] A cylinder block having a plurality of cylinder bores; a cylinder head fixed to an end surface of the cylinder block via a valve plate; a low-pressure chamber formed in the cylinder head; A plurality of suction ports for communicating the low-pressure chamber with the cylinder bore; and a plurality of suction valves for opening and closing the plurality of suction ports, wherein both the number of the suction ports and the number of the suction valves are the same as those of the cylinder bore. In a reciprocating refrigerant compressor equal in number, the suction port is divided into a plurality of holes by ribs. 2. The reciprocating refrigerant compressor according to claim 1, wherein said rib is formed substantially radially from a central axis of said cylinder bore. 3. The reciprocating refrigerant compressor according to claim 1, wherein a groove or a hole is formed on a surface of the rib.