JPH06341388A - Pressure valve - Google Patents

Abstract

PURPOSE: To simplify structure and to lower a cost by forming a valve tongue piece of a thin piece in a valve member matching a valve opening, constructing a valve member supporting body having a stroke catching member restricting an opening stroke of the thin piece as a sleeve, and forming a groove for inserting the valve tongue piece. CONSTITUTION: This pressure valve, a discharge valve 30 especially, is applied to a compressor provided with a rotational piston 39, and at least a valve member supporting body is provided with a stroke catching member restricting an opening stroke of a thin piece. In this case, the valve member supporting body is formed as a sleeve 38. In the circumference of the sleeve 38, an axial groove 44 and circumferential grooves 41-43 are formed. On the other hand, circular arc type valve tongue pieces 51-53 are formed by thin pieces in a valve member 37, and the valve tongue pieces 51-53 are inserted into the circumferential grooves 41-43 and connected to a lateral web 50 held inside the axial groove 44. The supporting sleeve 38 is fitted inside a valve chamber 28. In addition, stroke stoppers for the valve tongue pieces 51-53 are formed by the bottom parts of the circumferential grooves 41-43 within the ranges of valve openings 31-33.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION The present invention relates to a pressure valve for a compressor having a rotating piston, such as a rotary piston compressor or a vane compressor, of the type described in the preamble of the first claim. In particular, it relates to a discharge valve.

[0002]

In the case of the known pressure valve of the so-called circular construction type of the type mentioned at the outset (DE 3515 239 C2), the valve body is formed by a valve sleeve having a number of valve slits. A large number of protrusions are provided on the inner peripheral surface of the valve sleeve between the valve slits. Each valve slit is surrounded by a valve seat. The cylindrical valve member is arranged inside the valve sleeve and comprises a number of lamellas corresponding to the number of valve slits, each lamella touching one valve seat. The valve member is received and positioned by a valve member support located within the valve sleeve. The valve member support is formed with a substantially double T-shaped cross section, one transverse web supporting the valve member and the other transverse web at a distance of the stroke. A stroke-capturing member is formed for limiting the stroke of the flakes, which are located in front of the wall surface and contact the valve seat with a spring preload.

Such a pressure valve of circular construction is pushed into the axial bore of the compressor's stroke ring, which encloses the compression chamber in a gas-tight manner with a compression piston rotating in the compression chamber. The axial hole is connected to the compression chamber via a connection hole. Such a rotary piston compressor with a circular structure type discharge valve is described in DE 380551.
7A1 specification.

The advantage of using a circular discharge valve in a compressor with a rotating compression piston is that the stroke ring does not need to be provided with a specially sealed valve cover. Such valve covers have been unavoidable in the case of pressure valves of the conventional construction type which are inserted into the radial bore. In addition, due to the circular design, the wall thickness of the stroke ring between the compression chamber and the axial bore for receiving the discharge valve is significantly reduced and thereby the waste space of the discharge valve is kept small.

[0005]

An advantage of the pressure valve according to the invention having the features of claim 1 is that the structure is simple and the associated manufacturing costs are reduced. Furthermore, the pressure valve is formed only from two assembly parts, namely the valve part and the support sleeve, which are simply assembled and pushed into the axial bores already provided in the stroke ring. By eliminating the valve sleeve, the dead space of the pressure valve is significantly reduced compared to known pressure valves. The valve tongues work without friction and thus allow high operating frequencies.

Advantageous configurations and improvements of the pressure valve according to claim 1 are obtained by the features of the other claims.

[0007]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT A two-passage vane compressor, shown in cross section in FIG. 1, of a compressor with a rotating piston for a refrigerant circuit of a vehicle air conditioner shown as an example is a compression chamber. It has a stator 10 with a stroke ring 12 surrounding 11 and a rotor 13 rotating in a compression chamber 11, the rotor 13 being driven by an internal combustion engine of a motor vehicle, for example.

The compression chamber 11 is closed on the end face side by a side plate 14 which is hermetically screwed to the stroke ring 12. Two working chambers 15 and 16 are formed in the compression chamber 11 between the rotor 13 and the stroke ring 12, and these working chambers are arranged one behind the other in the rotation direction (arrow 17) of the rotor 11. There is.

Both working chambers 15 and 16 are of identical construction and have a variable radial width over the circumferential direction, which in this case is the chamber when viewed in the direction 17 of rotation of the rotor. It increases from the beginning to the center of the chamber and decreases from the center to the end of the chamber. In this case, the radial width of the working chamber is determined by the inner wall 18 of the stroke ring 12, which extends trochoidally about the rotor axis 19 in the region of the working chamber.

Both working chambers 15 and 16 have two sealing strips 2.
0, 21, which are hermetically separated from one another, this sealing strip is inserted in the appropriate longitudinal groove 22, 23 of the stroke ring 12 and in the region of the narrowest gap between the stroke ring 12 and the rotor 13. Is in contact with the rotor 13.

The cylindrical rotor 13 has four vanes 24 as a whole, which vanes slide in a longitudinal slit 25 extending parallel to the rotor axis and extending radially to the peripheral surface of the rotor. It is movably inserted.

The ends of the vanes 24 facing the groove bottom each limit a pressure chamber 26 in one vertical slit 25, which pressure chamber is larger than the suction pressure of the refrigerant and higher than the compression pressure of the refrigerant. It is filled with a small predetermined pressure applied refrigerant.

Under the action of this pressure, a vane 24, which is movable in the radial direction with its longitudinal axis oriented parallel to the rotor axis, has its free end projecting from the longitudinal slit 25 at the inner wall 18 of the stroke ring 12. Contacting the rotor and rotating the rotor, the working chambers 15 and 16 are connected to the suction chamber 15 with a variable volume.
1 or 161 and compression compartment 152, or 162
Split into.

Each of the working chambers 15 and 16 has a fluid inlet (not shown) at the chamber inlet and a fluid outlet 2 at the chamber outlet.
Have 7. Of the fluid outflow portions of both working chambers 15 and 16, only the fluid outflow portion 27 of the working chamber 15 is shown.
As is apparent from the cross-sectional view of FIG. 2, the fluid outflow portion has three outflow openings 271, 27 arranged side by side in the axial direction at intervals.
2, 273.

An axial bore 28 is formed in the stroke ring 12 near the fluid outlet 27, and three axially juxtaposed valve openings 31, 32, 33 are provided in the axial bore 28. ing. The respective valve openings 31, 32, 33 are connected to the fluid outlet 27 of the working chamber 15 through the holes 34, 35, 36.
Are connected to the outflow openings 271, 272, 273.
The same axial bore with the same valve opening is also provided in the fluid outlet of another working chamber 16.

The stroke ring 12 with the axial bore 28 forms the valve body of a pressure valve or discharge valve 30 which is arranged downstream of the fluid outlet 27, the pressure valve or discharge valve further comprising a valve member 37.
(See FIGS. 2 and 5) and support sleeve 38 (see FIGS. 2 and 4). The support sleeve is inserted into the axial bore 28 by a light press fit and positions the valve member 37 within the axial bore 28.

The rotation of the support sleeve in the axial hole 28 is performed by rotating the end surface of the support three 38 and one side plate 14 of the stator 10.
The axial movement of the support sleeve 38 is blocked by the side plates 14 of the stator 10 which come into contact with the end faces of the support sleeve, while being blocked by the securing pin 39 between the support sleeve 38 and the support pin 38. The inner sleeve wall of the support sleeve 38 is shaped into a polygon 40 (see FIGS. 3 and 4) at one end face in order to positionably insert the support sleeve 38 into the axial bore 28.

On the peripheral surface of the support sleeve 38 there is, on the one hand, an axial groove 44 extending over the entire length of the support sleeve, and
On the other hand, three annular grooves 41, 42, 43 are provided which start from the axial groove and extend laterally in the circumferential direction relative to the axial groove. The mutual spacing of the three annular grooves 41, 42, 43 is chosen such that one annular groove 41, 42, 43 respectively covers the valve openings 31, 32, 33 in the axial bore 28.

In this case, the respective valve openings 3, 32, 3
Since 3 is surrounded by valve seats 45, 46, 47, the axial width of the annular grooves 41, 42, 43 is designed to be slightly larger than the outer valve seat diameter. The valve member 37 includes three valve tongues 51, 52, which are spaced apart from each other and extend in parallel.
Formed of 53, the valve tongue is integrally connected to the transverse web 50 at the bottom of the tongue.

The axial spacing of the valve tongues 51, 52, 53 is the axial spacing of the annular grooves 41, 42, 43 and the valve opening 31 ,.
The axial spacing of 32, 33 corresponds to each other. The dimensions of the valve member 37 in this case are such that the transverse web 50 is inserted without play in the axial groove 44 and the valve tongues 51, 52, 53 are inserted with play in the annular grooves 41, 42, 43. Has been selected.

Since the thickness of the valve member 37 corresponds approximately to the groove depth of the axial groove 44, the transverse web 50 is inserted in the axial groove 44 in the same plane. In this case, the length of the valve tongue is chosen such that it extends over a circumference slightly less than half the circumference of the support sleeve 38.

The groove depth of the annular grooves 41, 42, 43 is approximately 1
It is constant over a central angle of 80 degrees and is approximately the same as the groove depth of the axial groove 44. In this range of constant groove depth, the axial grooves 44 are annular grooves 41, 42, 4
Cross 3

Annular groove 4 over another central angle of approximately 90 degrees
The groove depth of 1, 42, 43 increases continuously up to the maximum depth given by the desired travel of the end sections of the valve tongues 51, 52, 53 and then continuously to a more constant groove depth. Has decreased.

In this case, the groove bottoms of the annular grooves 41, 42, 43 are so-called stroke catching members, that is, valve tongue pieces 51, 52, 53 for limiting the opening stroke of the valve tongue piece when the discharge valve 30 is opened.
Forming a stopper for. Each annular groove 41, 4
Radial holes passing through the sleeve wall communicate with the bottoms of the holes 2, 43. Of these radial holes, only the radial hole 54 is shown in FIG. 2 and only the radial hole 55 is shown in FIG. .

In this case, the radial holes 54, 55 have valve tongue pieces 51, 52, in the range of the groove bottom where the radial holes are enlarged.
It is arranged so that it lies outside the annular groove section covered by 53. In this case, the radial groove is arranged substantially diametrically with respect to the axial groove 44.

A valve member 37 for assembling the discharge valve 30.
(FIG. 5) is inserted into the axial groove 44 and the annular grooves 41, 42, 43 of the support sleeve 38 (FIG. 4) so as to be flush with each other. The support sleeve 38 is then pushed together with the inserted valve member 37 into the axial bore 28, and the pivoting of the support sleeve 38 causes the spring-elastic valve tongues 51, 5 to move.
2,53 ends with preload valve seats 45,46,
Positioned to contact 47 (FIGS. 2 and 3). The support sleeve 38, which is held in the axial bore 28 by means of a light press fit, is then fixed by the retaining pin 39 in the additionally obtained position.

When the gas pressure in the working chamber 15 of the compression chamber 11 exceeds a predetermined outflow pressure, the valve tongue pieces 51, 52, 53.
Is lifted from the valve seats 45, 46, 47 and compressed by the valve openings 31, 32, 33, the annular grooves 41, 42,
43 and the support sleeve 3 via the radial holes 54, 55
8 into and from the pressure chamber or pressure conduit of the compressor.

A modified pressure or discharge valve 30 'is shown in FIGS. 6 and 7, in which case FIGS.
The same reference numerals are given to the components corresponding to the pressure valves of the above. In this case, in the modified embodiment of the pressure valve 30 of FIGS. 2 and 3, the annular grooves 41 ', 42', 43 'are the support sleeves 3.
8'is formed with the same constant groove depth equal to the thickness of the valve member 37 over the entire circumferential direction.

Within the axial groove 28 there are provided three notches 56, 57, 58 axially spaced from one another, which notches substantially in the region of the valve openings 31, 32, 33. It extends over a central angle of 180 degrees. The axial spacing of the notches corresponds to the axial spacing of the annular grooves 41 ', 42', 43 ', so that the annular grooves are aligned with the notches. The cutting depth continuously increases from the starting end of the cutting portion toward the center of the cutting portion and decreases continuously again from the center of the cutting portion toward the end of the cutting portion. The maximum depth of cut is predetermined by the required stroke of the valve tongues 51, 52, 53.

The valve openings 31, 32, 33 are provided at the bottoms of the notches 56, 57, 58, respectively. Furthermore, the structure and mode of operation of the pressure valve of FIGS. 6 and 7 is consistent with the pressure valve described in FIGS. At the time of assembly, the support sleeve 38 ′ together with the inserted valve member 37
It is rotated 80 degrees and pushed axially into the axial bore 28 and then rotated into the correct position.

In this case, the valve tongues 51, 52, 53 are swiveled into a notch cut into the axial bore 28 of the stroke ring 12 and the end section of the valve tongue in this case is valve opening 3
The valve seats 45, 46, 47 surrounding 1, 32, 33 are contacted with a preload.

The advantage of the pressure valve of this embodiment is that the holes 34, 35, 3 are formed by the notches ground in the stroke ring 12.
This means that the hole length of 6 is shortened and, consequently, the dead space volume of the pressure valve is further reduced as compared with the embodiment of FIGS.

8 and 9, the pressure valve 30 "shown in FIGS. 8 and 9 is likewise designated by the same reference numeral as that which corresponds to the pressure valve of FIGS. 2 and 3. The support sleeve 38 "is made by casting or powder metallurgical pressing with only slight post-processing.

The sleeve wall of the support sleeve has two end-side circular rings 60, 61 which are connected to each other by means of an axial transverse web 65 (FIG. 9), and 3 which project integrally from the axial web. The number of arc members 62, 63, 64 is reduced. The arc member is designed to be slightly longer than the valve tongue pieces 51, 52, 53.

The remaining transverse web 65 supports the axial groove 44 and the arcuate members 62, 64 each have one annular groove 4.
1, 42, 43 are supported, and this annular groove is formed as shown in FIGS. 2 and 3 with variable groove depth. The radial groove is omitted. In that case, however, this area of the sleeve wall is lacking and this causes the valve opening 31,
This is because a connection to the central opening from 32, 33 to the pressure chamber and pressure conduit of the compressor is obtained. Furthermore, the construction and mode of operation of the pressure valve of this embodiment is consistent with the pressure valve of FIGS.

In the case of the pressure valve 38 "according to FIGS. 8 and 9, the annular grooves 41, 42, 43 are arranged in the pressure valve 3 according to FIGS.
As in the case of 8 ', it may be constructed with a constant groove depth and for this purpose suitable cutouts may be provided in the axial bore 28.

The invention is not limited to the illustrated embodiment. It is also possible to use pressure valves different from the described use, in particular in a compressor, for example a vane compressor or a rotary piston compressor.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of a two-channel vane compressor having a pressure valve inserted in the stroke ring.

2 is a side view of the inserted pressure valve, FIG.
Partial cross-sectional view along the line ll.

FIG. 3 is a sectional view taken along the line lll-lll in FIG.

FIG. 4 is a schematic perspective view of a support sleeve of a pressure valve.

FIG. 5 is a schematic perspective view of a valve member of a pressure valve.

FIG. 6 is a view corresponding to FIG. 2 of a pressure valve of another embodiment.

FIG. 7 is a view corresponding to FIG. 3 of a pressure valve of another embodiment.

FIG. 8 is a view corresponding to FIG. 2 of the pressure valve of the third embodiment.

9 is a view corresponding to FIG. 3 of the pressure valve of the third embodiment.

[Explanation of symbols]

10 stator, 11 compression chamber, 12 stroke ring, 13 rotor, 14 side plate, 15, 16 working chamber, 17 rotation direction, 18 inner wall, 19 rotor axis, 20, 21 sealing strip, 22, 23 vertical groove,
24 vanes, 25 vertical slits, 26 pressure chambers, 27 fluid outlets, 28 axial holes, 30,
30 'pressure valve or discharge valve, 31, 32, 33 valve opening, 34, 35, 36 hole, 37 valve member, 3
8, 38 ', 38 "support sleeve, 39 securing pin, 40 polygonal part, 41, 42, 43, 41',
42 ', 43' annular groove, 44 axial hole, 45,
46,47 valve seat, 50 lateral web, 51,52,
53 valve tongue, 54, 55 radial holes, 56, 5
7,58 Notch, 60,61 Circular ring, 6
2, 63, 64 arc member, 65 horizontal web, 15
1,161 suction compartment, 152,162 compression compartment

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Claudius Muschel Knautz Federal Republic of Germany Rauf Aspichstrasse 15

Claims (11)

[Claims] 1. A pressure valve for a compressor with a rotating piston, such as a rotary piston compressor or a vane compressor, in particular a discharge valve, which is radially transversal into a valve body having a cylindrical valve chamber. At least one valve opening is formed which opens with a surface axis, the valve member having a number of spring-elastic lamellas corresponding to the number of valve openings, each lamella surrounding the valve opening with a preload. Where the valve member support is in contact with the valve seat and the valve member support has a stroke capture member that limits the opening stroke of the at least one lamina, the valve member support having the stroke capture member has a sleeve (38; 38 ′; 38 ″), the sleeve being provided on the peripheral surface with axial grooves (4
4) and, on the other hand, at least one circumferential groove (41, 42, 43; 41 ', 42', 43 ') which starts from the axial groove (44) and extends transversely to the axial groove. And has a circumferential groove having an axial width greater than the outer valve seat diameter and at least one of the valve members (37).
The two flakes form an arcuate valve tongue (51, 52, 53) which has a play with at least one circumferential groove (41, 42, 43, 41 ', 42', 4).
3 ') which is inserted into the axial groove (44) in the tongue extension and is retained in the axial groove (44) without play.
0) and is integrally connected to the support sleeve (38; 3
The outer diameter of 8 '; 38 "is equal to that of the support sleeve (38; 3
8 '; 38 ") is designed to be inserted into the valve chamber (28) without play and at least one circumferential groove (41,42,43,; 41', 42 ', 43') Pressure valve, the groove bottom of which forms a travel stop for the free end of at least one valve tongue (51, 52, 53) in the region of the valve opening (31, 32, 33). 2. Pressure according to claim 1, characterized in that the transverse web (50) of the valve member (37) is inserted in the axial groove (44) so as to be coplanar in the circumferential direction. valve. 3. The groove depths of the circumferential grooves (41, 42, 43) are substantially constant over a central angle of about 180 degrees and to the groove depth defined by the valve tongue stroke in the remaining angular range. A continuous increase over a central angle of 90 degrees and then a continuous decrease again to a constant value, the axial groove (44) being at least one circumferential groove (41, 42, 43) Located in the central angle range with a constant groove depth of at least one valve tongue (51, 52, 53) such that the free tongue end has a maximum groove depth of the circumferential groove. Pressure valve according to claim 1 or 2, characterized in that it is designed to lie in range. 4. The groove depth of the circumferential grooves (41 ', 42', 43 ') is constant over the entire central angle range and approximately corresponds to the thickness of the transverse web (50) and the valve tongue. And at least one semi-ring-shaped groove starting from the valve chamber in the valve body (12) and aligned with at least one circumferential groove (41 ', 42', 43 ') in the support sleeve (38). -Shaped notches (56, 57, 58) are provided, the axial width of which is at least equal to the axial width of at least one circumferential groove (41 ', 42', 43 '). And the depth of cut of the cut portion continuously increases from the start end of the cut portion toward the center of the cut portion and continuously decreases from the center of the cut portion toward the end of the cut portion. 57, 58) is the maximum depth of cut at the bottom of the cut The pressure valve according to claim 1 or 2, wherein the pressure valve is located in the range. 5. At least one circumferential groove (41, 42, 43, 41 ', 42', 4) of the support sleeve (38).
3 ') a radial hole (54, 5) through the sleeve wall
5) is open and this radial hole allows the valve opening (31,
32, 33) located outside the groove segment of the circumferential groove covered by the valve tongues (51, 52, 53). The pressure valve described. 6. At least one radial hole (54, 5)
Pressure valve according to claim 5, characterized in that 5) is provided in the support sleeve (38) diametrically with respect to the axial bore (44). 7. An axial web (65) and at least one starting integrally from the axial web, in which the sleeve wall of the support sleeve (38 ″) joins the two end circular rings (60, 612) together. Arc member (62, 63, 6
4) and axial grooves (44) and circumferential grooves (41, 42, 43) are formed in the axial web (65) and arc members (60, 61, 62, 63, 64). The pressure valve according to any one of claims 1 to 4, characterized in that 8. Pressure valve according to claim 7, characterized in that the support sleeve (38 ″) is manufactured by a casting method or a pressing method. 9. Support sleeve (38; 38 '; 38 ")
9. The pressure valve according to claim 1, wherein a polygonal portion is formed on the inner sleeve wall at one end surface of the pressure valve. 10. Support sleeve (38; 38 '; 3)
8 ″) additionally via the securing pin (39) to the valve body (1
Pressure valve according to any one of claims 1 to 9, characterized in that it is prevented from turning in 2). 11. The stroke ring (1) of a compressor, such as a rotary piston compressor or a vane compressor, having a valve body.
2), this stroke ring together with the compression piston (13) rotating in the compression chamber (1
1) surrounding at least one valve opening (3
Pressure valve according to any one of claims 1 to 10, characterized in that (1, 32, 33) is connected to the compression chamber (11) via a hole (34, 35, 36).